JPH06296401A - Forward / reverse working machine - Google Patents

Abstract

(57) [Summary] [Purpose] While reducing the number of parts and downsizing the forward / reverse mechanism that drives the forward and reverse claws in opposite directions,
Reduce the load on the work axis. A pair of left and right forward rotation work shafts 123L, which support forward rotation pawls, are provided on the outer periphery of a reverse rotation work shaft 124 that supports the reverse rotation pawls.
The 123R is coaxially fitted. A work counter shaft 125 arranged in front of the reverse rotation work shaft 124 and the forward rotation work shafts 123L and 123R is connected to a transmission via an endless chain 130 and driven. Work counter shaft 1
25 and the reverse rotation work shaft 124 are connected via an endless chain 133, and the work counter shaft 125 and the forward rotation work shaft 12 are connected.
3L and 123R are connected via a pair of gears 134 and 135.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a casing in which a forward working shaft having a forward working member and driven in the forward direction and a reverse working shaft having a reverse working member and driven in the reverse direction are coaxial with each other. The present invention relates to a forward / reverse working machine. The working machine here is
Walk-type tiller (including walk-type managed tiller and rotor tiller), riding-type tiller (including ride-controlled tiller), snowplow, reel mower-type lawn mower Etc.

[0002]

2. Description of the Related Art A forward / reverse working machine of this type is known as an actual Kaihei 4-35.
It is known from Japanese Patent Publication No. 03.

The above-mentioned conventional forward / reverse working machine uses a planetary gear mechanism. A sun gear is fixed to one of a forward rotating work shaft and a reverse rotating work shaft coaxially arranged, and a ring gear is fixed to the other. Furthermore, the planetary gear that meshes with the sun gear and the ring gear is supported by the casing.

[0004]

By the way, in the above-described conventional forward / reverse working machine, the use of the planetary gear mechanism not only increases the number of parts and complicates the structure, but also houses the planetary gear mechanism. There is a problem that the size of the casing becomes large, the number of remaining plowed parts increases, soil accumulates on the front surface of the casing, and the airframe easily stacks.

The present invention has been made in view of the above circumstances, and an object thereof is to provide a forward / reverse working machine having a simple structure, a small size and a light weight.

[0006]

In order to achieve the above-mentioned object, the invention described in claim 1 includes a forward rotation work shaft which is forwardly driven and has a forward rotation work member, and a reverse rotation work member. In a forward / reverse working machine that has a reverse working shaft that is driven in reverse and is coaxially supported by a casing, a work counter shaft that is connected to and driven by a prime mover is provided near the forward and reverse working shafts. , One of the two work shafts is connected to the work counter shaft through an endless chain to rotate in the same direction as the work counter shaft, and the other of the two work shafts is connected to the work counter shaft through a gear to It is characterized in that it is rotationally driven in the direction opposite to the work counter shaft.

According to a second aspect of the present invention, in addition to the structure of the first aspect, the left normal rotation working member and the reverse rotation working member, and the right side normal rotation working member and the reverse rotation working member are connected to the casing. It is characterized in that it is symmetrically arranged on both the left and right sides.

According to the invention described in claim 3, in addition to the structure of claim 2, the left and right forward rotation working members are arranged adjacent to the casing, and the left and right forward rotation working members are disposed outside the left and right forward rotation working members. It is characterized in that a reversing work member of is arranged.

In addition to the structure of any one of claims 1 to 3, the invention according to claim 4 is characterized in that a pair of right and left cylindrical forward rotation work shafts are coaxially fitted to the outer periphery of the reverse rotation work shaft. , Between the two forward rotation work shafts, the reverse rotation work shaft is connected to the work counter shaft by an endless chain to drive the work piece in the reverse direction, and both forward rotation work shafts are connected to the work counter shaft by gears on the left and right sides of the endless chain. It is characterized by being driven in the normal direction.

In addition to the structure of any one of claims 1 to 3, the invention described in claim 5 is such that a pair of left and right cylindrical forward rotation work shafts are coaxially fitted to the outer periphery of the reverse rotation work shaft. Between the both forward rotation work shafts, the reverse rotation work shaft is connected to the work counter shaft with a gear for reverse rotation drive, and both the forward rotation work shafts are connected to the work counter shaft with an endless chain on the left and right sides of the gear to forward the work. It is characterized by being rotationally driven.

The invention described in claim 6 is characterized in that, in addition to the structure of any one of claims 1 to 3, the rotational speeds of the forward rotation work shaft and the reverse rotation work shaft are set to be substantially equal.

The invention described in claim 7 is characterized in that, in addition to the structure according to any one of claims 1 to 3, the diameters of the forward rotation working member and the reverse rotation working member are set substantially equal to each other.

[0013]

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

1 to 12 show a first embodiment of the present invention. FIG. 1 is an overall side view of a walking type tiller, FIG. 2 is a two-direction arrow view of FIG. 1, and FIG. 2 and 3 direction arrow view, FIG.
4 is a sectional view taken along line 4-4 of FIG. 2, FIG. 5 is a sectional view taken along line 5-5 of FIG. 4, FIG. 6 is a sectional view taken along line 6-6 of FIG. 4, and FIG. 7 is 7-7 of FIG.
4 is a sectional view taken along line 8-8 in FIG. 4, FIG. 9 is a view taken in the direction of arrow 9 in FIG. 4, FIG. 10 is a view taken in the direction of arrow 10-10 in FIG. 9, and FIG. FIG. 12 is a 12-direction arrow view of FIG. 4.

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 top of the mission case 1, and a shift lever 11 extends rearward of the machine body through the shift lever guide plate 10. 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, there is provided a rotary working machine 19 having left and right forward rotation pawls 17 _{1 to} 17 ₃ and left and right reverse rotation pawls 18 ₁ to 18 ₃ . The upper surface of the rotary working machine 19 is covered with a rotary cover 20, and a rear part of the rotary cover 20 is provided with a resistance rod 21 whose vertical position is adjustable and a leveling plate 22 which is vertically swingable. It is also possible to reverse the rotation directions so that the normal rotation claws 17 _{1 to} 17 ₃ become reverse rotation claws and the reverse rotation claws 18 ₁ to 18 ₃ become forward rotation claws.

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 biased 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 mentioned 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 FIG. 4, in 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 an aluminum alloy are split in the center of the machine body. They are joined together and the outer peripheral portion is fastened with a plurality of bolts 53. The handle column 13 is pivotally supported on the mission case 1 so as to be vertically swingable.

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 main shaft 35 in the mission case 1 at an obliquely upper rear position. 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 FIG. 12 as well, a plate 70 welded to the lower end of the shift lever 11 is shown.
Are two pins 71, 72 on the upper surface of the mission case 1.
It is pivotally supported via a shaft, and its swing locus is restricted by a guide groove 10 ₁ formed in the shift lever guide plate 10 in the lateral direction of the machine body. Mission case 1
A boss portion 73 ₁ formed at the right end of the connecting member 73 having a U-shaped cross section is coupled to the right end of the shift rod 67 protruding outward from the right side surface of the shift rod 67 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.

On the secondary shaft 66, a rotary driven gear 84 and a rotary drive sprocket 85, which are integrally formed, are rotatably supported via a needle bearing, and the shift rod 73 is located 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 rotatably supported via a needle bearing. The counter shaft 64 includes 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 travel 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, which support wheels W, W at their 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 opposite ends thereof, and a differential gear sprocket 106 for traveling fixed to a differential box 105 of the differential gear 104 and a drive sprocket 92 for traveling provided on the counter shaft 64 are 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, normally, 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 the rear end of the expanded portions 51 ₃ of 52 ₃ intended to be accommodated in a pair of left and right forward working axis 123L supported coaxially of the ball bearings 122 and 122, 123R and the left and right forward rotation work shafts 123
It is provided with one reverse working shaft 124 penetrating the L and 123R so as to be rotatable relative to each other and extending to the left and right.

A work counter shaft 125 is supported in front of the forward rotation work shafts 123L and 123R and the reverse rotation work shaft 124 via a pair of ball bearings 126 and 126. The rotary driven sprocket 129 fixed to the work counter shaft 125 and the rotary drive sprocket 85 are connected via an endless chain 130. The first sprocket 131 fixed to the work counter shaft 125 and the second sprocket 132 fixed to the reverse rotation work shaft 124 are connected by an endless chain 133, whereby the reverse rotation work shaft 124 reverses in the same direction as the work counter shaft 125 (rotary). The work machine 19 is driven in the opposite direction).

On the other hand, the pair of first gears 134, 134 provided at both ends of the work counter shaft 125 are a pair of second gears 135, 134 provided on the left and right forward rotation work shafts 123L, 123R.
135 mesh with each. Therefore, the double forward rotation work shaft 12
The 3L and 123R are driven in the forward direction (the same direction as the traveling direction of the rotary work machine 19) in the direction opposite to the work counter shaft 125 and the reverse work shaft 124.

The tooth ratio of the first sprocket 131 and the second sprocket 132 is the same as that of the first gears 134, 134 and the second gear.
The gear ratio is set to be equal to that of the gears 135, 135. Therefore, the rotation speed of the reverse rotation work shaft 124 and the normal rotation work shaft 12 are set.
The rotational speeds of 3L and 123R are equal to each other, and the rotational speeds are slightly reduced with respect to the rotational speed of the work counter shaft 125.

It should be noted that the forward / reverse rotation mechanism 121 is housed inside.
The enlarged portion 51 at the rear end of the session case 1 ₃, 52₃Left and right
Covered by pants 136, 136 divided into two
Be protected.

Thus, the rotation of one work counter shaft 125 to which the driving force of the engine E is transmitted is controlled by the endless chain 1.
Since it is transmitted to the reverse rotation work shaft 124 via 33 and is transmitted to the forward rotation work shafts 123L and 123R via the first gears 134 and 134 and the second gears 135 and 135, the number of parts is extremely small and simple. With the structure, the forward / reverse mechanism 121 can be made compact.

In particular, the reduction ratio of the power transmission path from the work counter shaft 125 to the normal rotation work shafts 123L and 123R,
Since the reduction ratios of the power transmission paths from the work counter shaft 125 to the reverse rotation work shaft 124 are set to be small,
The torque of the forward rotation work shafts 123L and 123R and the reverse rotation work shaft 124 becomes relatively small. Therefore, the first sprocket 131, the second sprocket 132, the endless chain 133, the first gears 134 and 134, and the second gear 135,
It is possible to downsize the 135, and thereby the forward / reverse rotation mechanism 121 can be further downsized. As a result, the mission case 1 housing the forward / reverse rotation mechanism 121.
The rear end portion can be downsized, the minimum ground clearance of the portion can be sufficiently secured, and the residual tillage portion can be reduced as much as possible, and the stacking of the airframe can be effectively prevented.

Next, based on FIGS. 9 to 11, the forward rotation claws 17 _{1 to} 17 ₃ and the reverse rotation claws 18 ₁ to ₁ of the rotary working machine 19 are described.
8 ₃ will be described.

Sleeves 138 and 138 are fixed to the outer peripheries of the pair of left and right forward rotation work shafts 123L and 123R extending outward from the mission case 1, respectively. Two brackets 139 and 140 axially separated from each other are welded to the outer periphery of each sleeve 138, and two forward rotation pawls 17 ₁ and 17 ₂ are bolted to the bracket 139 inside the machine body. One forward claw 17 ₃ is bolted to the bracket 140 on the outside of the machine. The tips of the _three forward rotation claws 17 _{1 to} 173 arranged at 120 ° intervals are curved to the delay side in the rotation direction (see FIG. 10). Further, one of the three forward rotation pawls 17 _{1 to} 17 ₃ has a tip of the forward rotation pawl 17 ₁ curved toward the inside of the machine body, and the remaining two forward rotation pawls 1 1
The tips of 7 ₂ and 17 ₃ curve toward the outside of the machine.

The sleeve 1 is provided on the outer circumference of both ends of the reversing work shaft 124 extending outward from the mission case 1.
41 and 141 are fixed. Are two brackets 142, 143 spaced axially welded to the outer circumference of each sleeve 141, the reverse rotation pawl 18 _first one is bolted to the body inside the bracket 142, the aircraft outside of the bracket 143 The two reverse claws 18 ₂ and 18 ₃ are bolted. Three reverse claws 18 ₁ arranged at 120 ° intervals
To 18 ₃ of the tip in the direction of rotation behind the side, that is curved and the three Seitentsume 17 _{1-17 3} in the opposite direction (see FIG. 11). Furthermore, the tips of the _two reverse claws 18 ₂ and 18 ₃ among the _three reverse claws 18 ₁ to 18 ₃ are curved toward the inside of the machine, and the tip of the remaining one reverse claw 18 ₁ is outside the machine. Bend toward.

Thus, three forward rotation claws 17 ₁ are provided on the left side of the machine body.
To 17 ₃ and three with disposing the reverse rotation pawl 18 _{1-18 3,} Seitentsume 17 ₁ of three on the right side of the fuselage Symmetrically
Since the disposed to 17 ₃ and three reverse pawl 18 _{1-18 3} can tilling performance not only improves, prevents Dasshingu aircraft effectively. Moreover, since the number, diameter, and number of rotations of the forward rotation claws 17 _{1 to} 17 ₃ and the reverse rotation claws 18 ₁ to 18 ₃ are set to be equal, the forward rotation claw 17 ₁
~ 17 ₃ and the reverse rotation claws 18 ₁ to 18 ₃ are evenly driven, the loads on the forward rotation work shafts 123L and 123R and the reverse rotation work shaft 124 are made uniform, and the vibration is reduced, and the cultivated state is improved. As a result, dashing is prevented more effectively.

As is apparent from FIG. 4, the resistance rod 21 is attached to the rectangular tubular guide member 152 provided on 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 from this state and the belt tension clutch 36 is turned on, 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 64, 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 asked 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 transmitted to the work counter shaft 125 of the forward / reverse rotation mechanism 121 of FIG. 8 through the endless chain 130 and the rotary driven sprocket 129, and as described above, the forward rotation pawls 17 _{1 to} 17 ₃ and The reverse rotation claws 18 ₁ to 18 ₃ are rotationally driven.

[0054] By the way, Seitentsume 17 _{1-17 3} 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
~ 18 ₃ will bounce the soil forward. Therefore,
If the reversing claws 18 ₁ to 18 ₃ are arranged on the inner side in the width direction of the machine body, the soil that the reversing claws 18 ₁ to 18 ₃ have splashed forward is held by the front of the mission case 1 and the machine body may be stuck. is there. However, by placing the Seitentsume 17 _{1-17 3} inward in the width direction of the machine body and disposed reversely pawl 18 _{1-18 3} on the outside, reverse pawl 18 ₁
Since a sufficient distance is secured between ~ 18 ₃ and the mission case 1, the problem that the soil repelled by the reverse rotation claws 18 ₁ to 18 ₃ in the forward direction 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.

Referring to FIG. 5 again, when the shift rod 67 slides to the right from the "forward first speed + rotary work machine drive" position at the left end, 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" is reached.
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 64 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 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 64 → 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.

Next, a second embodiment of the present invention will be described with reference to FIG.

The work counter shaft 125 provided in the forward / reverse rotation mechanism 121 of the second embodiment is driven in the opposite direction (that is, in the forward rotation direction) to the work counter shaft 125 of the first embodiment. The rotation direction of the work counter shaft 125 can be changed by changing the design of the gear train in the transmission 61. The work counter shaft 125 and the reverse rotation shaft 124 are connected via the first gear 134 and the second gear 135, and the reverse rotation shaft 124 is rotationally driven in a direction opposite to the direction of the work counter shaft 125 rotating normally.
Further, the work counter shaft 125 and the left and right forward rotation shafts 123
L and 123R are respectively a pair of first sprockets 1
31, 131, the second sprockets 132, 132, and the endless chains 133, 133 are connected to each other, and the forward rotation shafts 123L, 123R are forward rotation work counter shafts 1.
It is rotationally driven in the same direction as 25.

Thus, according to the second embodiment as well, the first
It is possible to obtain the same effect as that of the embodiment.

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, the normal rotation work shafts 123L and 123R and the reverse rotation work shaft 124 can be rotated in opposite directions.

[0064]

As described above, according to the invention described in claim 1, the work counter shaft connected to the prime mover and driven is provided near the forward rotation work shaft and the reverse rotation work shaft, and both work shafts are provided. One of them is connected to the work counter shaft via an endless chain to rotate and drive in the same direction as the work counter shaft, and the other of both work shafts is connected to the work counter shaft via a gear to connect to the work counter shaft. By rotationally driving in the reverse direction, the forward rotation work shaft and the reverse rotation work shaft can be driven in opposite directions with a simple structure having a small number of parts. As a result, the casing supporting the forward rotation work shaft and the reverse rotation work shaft can be miniaturized to minimize the residual tillage portion, ensure a minimum ground clearance, and effectively prevent stacking of the airframe.

According to the invention described in claim 2,
By arranging the left normal rotation working member and the reverse rotation working member and the right right rotation working member and the reverse rotation working member symmetrically on both left and right sides of the casing, not only the tilling work performance is improved but also the dashing is performed. It can be effectively suppressed.

According to the invention described in claim 3,
Disposing the left and right forward rotation working members adjacent to the casing, and by disposing the left and right reverse rotation working members outside the left and right forward rotation working members, it becomes difficult for soil to be deposited on the front lower surface of the casing, It is possible to more effectively prevent the stacking of the airframe.

According to the invention described in claim 4,
A pair of right and left cylindrical forward rotation work shafts are coaxially fitted around the outer circumference of the reverse rotation work shaft, and the reverse rotation work shaft is connected to the work counter shaft with an endless chain between the forward rotation work shafts and is driven in reverse. By connecting both forward rotation work shafts to the work counter shafts by gears on both the left and right sides of the endless chain and driving them in the forward direction, the arrangement of the power transmission system in the casing can be rationalized and the casing can be further downsized. Without
The residual tillage treatment can be effectively performed.

According to the invention described in claim 5,
A pair of right and left cylindrical forward rotation work shafts are coaxially fitted around the outer circumference of the reverse rotation work shaft, and the reverse rotation work shaft is connected to the work counter shaft with a gear between the forward rotation work shafts and reversely driven. By connecting both forward rotation work shafts to the work counter shaft with an endless chain on both left and right sides of the gear and driving them in the forward direction, the layout of the power transmission system in the casing can be rationalized and the casing can be made smaller. Therefore, the residual tillage treatment can be effectively performed.

According to the invention described in claim 6,
By setting the rotation speeds of the forward rotation work shaft and the reverse rotation work shaft to be substantially equal, the loads on both work members can be made uniform, and more effective prevention of dashing and reduction of vibration can be achieved.

According to the invention described in claim 7,
By setting the diameters of the forward and reverse working members to be approximately the same, the load on both working members is made uniform, more effective prevention of dashing and reduction of vibrations are possible, and the plowing condition is good. Can be

[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 view taken along the line 10-10 of FIG.

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

FIG. 12 is a view taken in the direction of arrow 12 in FIG.

FIG. 13 is a diagram corresponding to FIG. 8 according to the second embodiment of the present invention.

[Explanation of symbols]

1 mission case (casing) 17 _{1 to} 17 ₃ forward rotation claw (normal rotation work member) 18 ₁ to 18 ₃ reverse rotation claw (reverse rotation work member) 123L forward rotation work shaft 123R forward rotation work shaft 124 reverse rotation work shaft 125 work counter shaft 133 endless chain 134 1st gear (gear) 135 2nd gear (gear) E engine (motor)

Claims (7)

[Claims] 1. A forward working member (17 ₁ to 17 ₃₎ forward driven forward working axis a (123L, 123R)
When, in the reverse working member (18 _{1-18 3)} reverse driven reversely working axis a (124) and formed by coaxially supported to the casing (1) forward and reverse working machine, the prime mover (E) A work counter shaft (125) which is connected and driven is provided in the vicinity of the forward rotation work shafts (123L, 123R) and the reverse rotation work shaft (124), and both work shafts (123
L, 123R; 124) one endless chain (13
3) is connected to the work counter shaft (125) to rotate in the same direction as the work counter shaft (125), and the other of the work shafts (123L, 123R; 124) is geared (134, 135). A forward / reverse working machine characterized by being connected to a work counter shaft (125) via a shaft and rotationally driven in a direction opposite to the work counter shaft (125). 2. The forward rotation working member (17 _{1 to} 17 ₃ ) on the left side
And reversing the working member (18 _{1-18 3),} the right forward working member (17 ₁ to 17 ₃₎ and reverse working member (18 ₁
18. The forward-reverse working machine according to claim 1, wherein 18 ₃ ) are arranged symmetrically on the left and right sides of the casing (1). Wherein the left and right forward working member (17 ₁ to 17 ₃₎
Was disposed adjacent to the casing (1), and characterized in that arranged right and left reverse working member (18 _{1-18 3)} on the outside of their left and right forward working member (17 ₁ to 17 ₃₎ The forward / reverse working machine according to claim 2. 4. A pair of left and right cylindrical normal rotation work shafts (123L, 123R) are coaxially fitted around the outer circumference of the reverse rotation work shaft (124), and reverse rotation is performed between the two normal rotation work shafts (123L, 123R). The work shaft (124) is connected to the work counter shaft (125) by an endless chain (133) to drive the work shaft in the reverse direction, and both the forward-working work shafts (123L, 123R) are connected to the gear ( Thirteen
The forward / reverse working machine according to any one of claims 1 to 3, wherein the forward / reverse working machine is connected to the work counter shaft (125) at 4,135) and is driven to rotate normally. 5. A pair of right and left cylindrical forward rotation work shafts (123L, 123R) are coaxially fitted around the outer circumference of the reverse rotation work shaft (124), and reverse rotation is performed between the both forward rotation work shafts (123L, 123R). The work shaft (124) is connected to the work counter shaft (125) by the gears (134, 135) and is driven in the reverse direction, and the both forward rotation work shafts (123L, 123R) are provided on the left and right sides of the gear (134, 135). The forward / reverse working machine according to any one of claims 1 to 3, wherein the forward / reverse working machine is connected to a work counter shaft (125) by an endless chain (133) and is driven to rotate normally. 6. The forward / reverse working machine according to claim 1, wherein the normal rotation work shafts (123L, 123R) and the reverse rotation work shaft (124) are set to have substantially the same number of rotations. 7. A forward working member (17 ₁ to 17 ₃₎ and reverse working member (18 _{1-18 3)} according to claim 1, characterized in that it has substantially equal to the diameter of according to any one Forward / reverse working machine.