JP3672456B2 - Full-cut walking cultivator - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a full-cut walking type tiller configured to eliminate residual plowing below a casing that houses a transmission system for an output shaft on which a tilling rotor is mounted.
[0002]
[Prior art]
Conventionally, in the full-cut walking type tiller as described above, for example, as disclosed in Japanese Patent Laid-Open No. 9-65702, the tilling claw of the inclined claw shaft acts on the field portion below the casing. The inclined boss that supports the inclined pawl shaft in a downwardly inclined posture is welded to the casing that houses the transmission system for the output shaft on which the tilling rotor is mounted.
[0003]
[Problems to be solved by the invention]
In other words, in the above-described prior art, when configuring a full-cut walking type tiller, it is necessary to prepare a dedicated casing integrated with an inclined boss that supports the inclined pawl shaft in a downwardly inclined posture. Therefore, there is room for improvement in constructing a full-cut walking type tiller easily and inexpensively.
[0004]
An object of the present invention is to enable a simple and inexpensive construction of a full-cut walking type tiller.
[0005]
[Means for Solving the Problems]
In order to achieve the above object, in the invention according to claim 1 of the present invention, a relay shaft in a horizontal posture, and an inclined boss in an outer downward inclined posture while being externally fitted to the relay shaft in a state allowing its rotation. An inclined claw unit comprising an inclined bracket provided and an inclined claw shaft fitted around the inclined boss in a state of rotating integrally with the relay shaft, the relay shaft being connectable to an output shaft for tillage, and The tiller rotor is configured to be connectable to the outer end side thereof, and the inclined bracket can be connected to the machine body in a non-rotating manner, and the anti-rotation connection is formed on a boss on the machine body side that supports the output shaft. The engagement portion is configured to be engaged with an engagement portion formed on the inclined bracket, and the inclined claw unit is attached to the output shaft by a single connecting pin, and by the attachment, The relay shaft and front Tilting pawl shaft and rotates integrally with the output shaft and the inclined bracket configured to coupled state rotationally fixed on the machine body side is maintained, the mounting positions of the connecting pins in the inclined pawl unit The tilting claw with respect to the coupling tool is such that there is no cultivating claw provided on the inclined claw shaft and a coupling tool for mounting the cultivating claw on the inclined claw shaft in the insertion / removal direction of the coupling pin. The position is shifted in the rotation direction of the unit .
[0006]
[Action]
According to the first aspect of the present invention, in a general non-full-cut walking type tiller in which residual tillage occurs below the casing, the inclined claw unit is relayed to the tilling output shaft to which the tilling rotor is directly connected. For full cut to eliminate residual tillage under the casing by connecting the shaft, connecting the tilling rotor to the outer end side of the relay shaft, and connecting the inclined bracket of the inclined claw unit to the machine body A walkable tiller can be constructed.
[0007]
In other words, the entire general non-full-cut walking type tiller is effectively used, and the inclined claw unit is simply interposed between the output shaft for the tiller and the tilling rotor by using their connection structure. With this configuration, a full-cut walking type tiller can be configured.
[0008]
In addition, when the inclined claw unit and the tilling rotor are removed, other work devices such as a scraping rotor and a cultivating rotor can be mounted as usual, so that versatility is not impaired by using a full cut.
In addition, it is possible to easily connect the tilt bracket to the anti-rotation connection as compared with the case of using a connecting tool such as a bolt, and the number of parts can be reduced because the connecting tool is not used. It will be easier.
[0009]
〔effect〕
Accordingly, it is not necessary to prepare a dedicated casing in which an inclined boss for supporting the inclined pawl shaft in a downwardly inclined posture is provided, and an inclined pawl unit is interposed on both the output shaft for tillage and the tilling rotor. Therefore, it is not necessary to newly provide a connecting structure for connecting the tilt bracket and the anti-rotation bracket so that the full-cut walking type tiller can be configured easily and inexpensively and parts management can be facilitated. It became so.
[0010]
According to a second aspect of the present invention, in the first aspect of the present invention, the engaging portion is formed to cover an oil seal interposed between the output shaft and the boss. .
[0011]
[Action]
According to the second aspect of the present invention, there is no need to provide a dedicated oil seal cover that covers the oil seal interposed between the output shaft and the boss. Therefore, the configuration can be simplified, the manufacturing cost can be reduced, and the parts management can be facilitated.
[0012]
〔effect〕
Accordingly, the full-cut walking type tiller can be configured more simply and inexpensively, and the parts management can be further facilitated.
[0013]
According to a third aspect of the present invention, in the first or second aspect of the present invention, the inclined claw shaft is provided with a winding preventing member.
[0014]
[Action]
According to the third aspect of the invention, since weeds and the like can be prevented from being wound around the inclined claw shaft, it is possible to save the trouble of removing weeds and the like wound around the inclined claw shaft.
[0015]
〔effect〕
Therefore, a full-cut walking type tiller capable of improving workability can be configured.
[0016]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[0017]
FIG. 1 shows an overall side view of a walking type tiller. This walking type tiller has an air-cooled vertical axis engine 1, a mission case 2 connected to the lower part of the engine 1, and a rear side. And a pair of left and right control handles 3 and a tilling rotor 4 serving as a propulsion wheel, which is an example of a working device disposed on both the left and right sides of the transmission case 2, and the like. Yes.
[0018]
As shown in FIGS. 2 to 4, the transmission case 2 includes a planetary speed reducer 5 using the output shaft 1 a of the engine 1 as a sun gear, and a longitudinal transmission shaft 6 disposed on the same axis P <b> 1 as the output shaft 1 a. Also, a bevel gear type transmission mechanism 7 mounted at the lower end of the longitudinal transmission shaft 6 is housed. Further, a lateral output shaft 8 that protrudes from the mission case 2 toward the left and right outer sides is disposed at the lower portion of the mission case 2. That is, the transmission case 2 is a casing that surrounds the transmission system for the output shaft 8.
[0019]
The planetary reduction device 5 includes an output shaft 1a, three planetary gears 9 that mesh with the splines of the output shaft 1a, planetary carriers 10 that support these planetary gears 9 at equal intervals, and meshing guides for these planetary gears 9. The planetary gear 10 is decelerated and transmitted to the planetary carrier 10 while revolving with the rotation of the output shaft 1a, so that the planetary carrier 10 has the same axis P1 as that of the output shaft 1a. It is designed to be driven at reduced speed around.
[0020]
As shown in FIG. 2 and FIG. 3, the ring gear 11 has a radial case between the outer periphery of the ring gear 11 and the inner periphery of the transmission case 2 that holds the ring gear 11 so as to have a centering action. 2 is mounted and supported, and a friction material is lined on the surface thereof. The transmission case 2 is equipped with an arc-shaped friction plate 12A disposed below the ring gear 11. The friction plate 12A is engaged with a recess 2a formed on the inner surface of the transmission case 2, A convex portion 12a is formed to prevent the friction plate 12A from rotating together with the ring gear 11. The engine 1 includes an arc-shaped friction plate 12B disposed above the ring gear 11, and the upper and lower friction plates 12A and 12B press the ring gear 11 in the vertical direction so that the ring gear 11 rotates relative to the transmission case 2. Riding that adjusts the pressure contact force of each friction plate 12A, 12B with respect to the ring gear 11 over the braking state that prevents the pressure contact and the non-braking state in which the pressure contact is released and the ring gear 11 is allowed to rotate relative to the transmission case 2 A cam-type operation mechanism 13 is provided. The operating mechanism 13 includes an upper friction plate 12B fixed by screws 13a and a vertically movable pressing member 13A, and an operating member 13B that adjusts the pressing amount of the pressing member 13A by turning around the vertical axis P2. The operation arm 13C that rotates integrally with the operation member 13B, and the spring 13D that urges the operation member 13B to return to a non-pressed state, and the like, and the operation arm 13C includes the left steering handle shown in FIG. The operation member 13B is linked to a wire so that the operation member 13B rotates to the side of pressing the pressing member 13A when the operation lever 14 is gripped to the steering handle 3 side.
[0021]
With this configuration, as the operating lever 14 is gripped and operated to the steering handle 3 side, the pressure contact force of the upper and lower friction plates 12A and 12B with respect to the ring gear 11 can be increased, and thereby the planetary gear is rotated while the ring gear 11 is rotated. The half transmission state in which the planetary gear 9 is revolved and the transmission state in which the planetary gears 9 are revolved while preventing the rotation of the ring gear 11 can be realized, and the transmission amount from the engine 1 to the tilling rotor 4 can be adjusted. Further, when the operation of the operation lever 14 to the steering handle 3 side is released, a non-braking state that completely allows the rotation of the ring gear 11 appears and the revolution of each planetary gear 9 is prevented. As a result, transmission from the engine 1 to the tilling rotor 4 is interrupted.
[0022]
That is, the ring gear 11, the upper and lower friction plates 12A and 12B, and the operation mechanism 13 constitute a main clutch 15 that intermittently transmits power from the engine 1 to the tilling rotor 4, and this main clutch 15 can be simply used as a transmission. Can be used.
[0023]
As shown in FIGS. 3 and 4, a transmission 16 is interposed between the planetary carrier 10 of the planetary reduction gear 2 and the longitudinal transmission shaft 6. The transmission 16 is a high-speed transmission state in which the vertical transmission shaft 6 is directly connected to the planetary carrier 10 by a shift operation in a direction along the vertical transmission shaft 6 of the shift member 16A that is spline-fitted to the vertical transmission shaft 6. The state can be switched between a state shown by a solid line in FIG. 4 and a low-speed transmission state (state shown by a two-dot chain line in FIG. 4) in which the longitudinal transmission shaft 6 is connected to the planetary carrier 10 via a pair of transmission gears 16B. It is configured. The shift member 16A is coupled to the transmission case 2 so as to swing together with the shift lever 17 supported by the transmission case 2 so as to swing back and forth around the horizontal axis P3. By shifting the fork 16 </ b> C up and down, the fork 16 </ b> C is shifted in the direction along the longitudinal transmission shaft 6.
[0024]
The pair of transmission gears 16 </ b> B are vertically supported shafts 19 erected at symmetrical positions around the longitudinal transmission shaft 6 in the transmission case 2 so as to be arranged around the planet carrier 10 at equal intervals. The outer fitting is mounted to be freely rotatable. Further, each transmission gear 16B is prevented from being displaced in the vertical direction by a plate 20 extending from the transmission case 2 to each support shaft 19.
[0025]
As shown in FIGS. 3 to 5, the bevel gear type transmission mechanism 7 includes a first bevel gear 6 </ b> A integrally formed at the lower portion of the longitudinal transmission shaft 6, and a second bevel gear 21 that meshes with the first bevel gear 6 </ b> A. Yes. The output shaft 8 has a two-part structure of a left output shaft portion 8A and a right output shaft portion 8B disposed on the same axis P4. Between the bevel gear type transmission mechanism 7 and the output shaft 8, a side clutch mechanism 22 that transmits the left and right output shaft portions 8A and 8B so as to be independently driven is interposed.
[0026]
The side clutch mechanism 22 includes a left and right cylindrical shaft 23 that rotates integrally with the second bevel gear 21, inner fitting portions 8 a and 8 b that are fitted into the cylindrical shaft 23 in the left and right output shaft portions 8 A and 8 B, and the cylindrical shaft 23. A transmission position engaged between the left and right through holes 23a, 23b formed in the peripheral portion and the recesses 8aa, 8ba formed in the outer periphery of the inner fitting portions 8a, 8b, and a non-transmission position separated from the recesses 8aa, 8ba The left and right non-holding positions permitting movement of one of the left and right transmission balls 24 to the non-transmission position, and the holding position for holding the respective transmission balls 24 in the transmission position. The left and right outputs can be obtained by sliding the holder 25 with a single shift fork 27 by means of a holder 25 slidable over and a pair of left and right springs 26 that urge the holder 25 back to the holding position. It is configured as a ball transmission type that can be switched between a state in which the portions 8A and 8B are integrally driven (see FIG. 4) and a state in which the left and right output shaft portions 8A and 8B are independently driven (see FIG. 5). It is disposed in the dead space S of the transmission mechanism 7.
[0027]
As shown in FIGS. 1 and 3, the shift fork 27 is arranged in the mission case 2 immediately before the longitudinal transmission shaft 6 so as to be rotatable around the longitudinal axis P <b> 5 in parallel with the longitudinal transmission shaft 6. The operation shaft 28 is fixed to the lower end of the operation shaft 28. A die-cast bevel gear 29 is connected to the upper end of the operation shaft 28 so as to rotate integrally around the vertical axis P5. The bevel gear 29 is meshed with a die-cast bevel gear 31 that rotates together with a linkage shaft 30 that is supported by the transmission case 2 so as to be rotatable around the front and rear axis P6. A balance-type linkage arm 32 is fixed to the outer end of the linkage shaft 30, and both ends of the linkage arm 32 are linked to a steering lever 33 provided on the right steering handle 3 by wire.
[0028]
With this configuration, when the steering lever 33 is swung in the right direction from the neutral position during work, the linkage arm 32 swings in the clockwise direction, whereby the shift fork 27 swings in the right direction, and the holder 25 Is attached to the right output shaft portion 8B by the thrust of the tilling rotor 4 attached to the left output shaft portion 8A. A right-turning state with the cultivating rotor 4 as a fulcrum can appear, and conversely, if the steering lever 33 is swung leftward from the neutral position during work, the linkage arm 32 swings counterclockwise. As a result, the shift fork 27 swings leftward, and the holder 25 is slid leftward to interrupt transmission to the left output shaft portion 8A, so that the right output shaft portion 8B The left output shaft portion 8 by the thrust of the attached tilling rotor 4 And to be able to emerge the left turning state to fulcrum tillage rotor 4 side mounted on. That is, during the turning operation, the turning operation such as the small turn of the airframe can be easily performed, so that the work efficiency can be improved.
[0029]
When the swinging operation of the steering lever 33 is released, the holder 25 is returned to the holding position by transmission of the pair of left and right springs 26 provided in the side clutch mechanism 22, and is transmitted to the left and right output shaft portions 8A and 8B. Accordingly, a straight traveling state can be revealed by the thrust of each tilling rotor 4 mounted on the left and right output shaft portions 8A and 8B.
[0030]
As shown in FIGS. 3 to 5, the transmission case 2 includes a cylindrical case main body 2 </ b> A connected to the lower portion of the engine 1 and a bottom wall member 2 </ b> B joined to the bottom of the transmission case 2, with the output shaft 8 as a boundary. It is configured in a two-divided structure that is divided vertically. With this configuration, it is possible to improve the mounting accuracy of the mission case 2 with respect to the engine 1 as compared with the case where the mission case 2 is configured in a left and right divided structure. Further, since the side clutch mechanism 22 is attached to the output shaft 8 in advance, it is attached to the transmission case 2 so that the assembly can be facilitated. The case main body 2A and the bottom wall member 2B are made of aluminum die casting that does not need to be machined, and are sealed by applying a bond to their mating surfaces. By the way, a ring-shaped groove may be formed on the mating surfaces to improve the sealing performance. A plurality of reinforcing ribs 2b are formed on the outer surface of the bottom wall member 2B.
[0031]
As shown in FIGS. 6 to 9, the tilling rotor 4 is connected to the left and right output shaft portions 8 </ b> A and 8 </ b> B via an inclined claw unit U. The inclined claw unit U includes a horizontal relay shaft 34 that is externally fitted to the left and right output shaft portions 8A and 8B, and an inclined boss 35A that is externally fitted to the relay shaft 34 in a state that allows rotation thereof and that is inclined downward. The inclined bracket 35 and the inclined claw shaft 36 that is rotatably fitted to the inclined boss 35A, and the like, and the relay shaft 34 is configured to rotate integrally with the left and right output shaft portions 8A and 8B. It is interlocked and connected by one connecting pin 37.
[0032]
As shown in FIGS. 6 and 9, the inclined bracket 35 is externally connected to the boss 2c of the mission case 2 formed so as to support the left and right output shaft portions 8A and 8B. It functions as an oil seal cover that covers the oil seal 38 interposed between the portions 8A and 8B and the boss 2c, and is engaged with each engaged portion 2ca that is formed to project from the upper portion and the left and right side portions of the boss 2c. In addition, an engagement portion 35B is provided so as to determine the mounting posture of the inclined bracket 35 and prevent rotation.
[0033]
As shown in FIGS. 6 to 8, the inclined claw shaft 36 is formed with a pair of notches 36 </ b> A that integrally rotate the inclined claw shaft 36 with the left and right output shaft portions 8 </ b> A and 8 </ b> B by engagement with the first connecting pin 37. At the same time, the tilling claw 36B acting on the field portion below the mission case 2 with the rotation is bolted. The notch 36A has a shape that allows the first connecting pin 37 to be twisted and displaced with respect to the inclined claw shaft 36 that is generated when the inclined claw shaft 36 in the inclined posture is rotated integrally with the left and right output shaft portions 8A and 8B. Is formed. Further, the inclined claw shaft 36 has a claw-shaped winding preventing member that prevents foreign matter such as weeds from entering the inclined claw unit U and wrapping the weeds etc. on the inclined claw shaft 36 as the rotation thereof. 36C and 36D are equipped.
[0034]
As shown in FIGS. 6 and 10, the tilling rotor 4 is interlocked with the second connecting pin 39 so as to be fitted on the outer end side of the relay shaft 34 in the inclined claw unit U and to rotate integrally with the relay shaft 34. The horizontal claw shaft 4A, the tilling claw 4B that rotates integrally with the horizontal claw shaft 4A, the wrapping prevention member 4C that surrounds the horizontal claw shaft 4A and prevents weeds and the like from being wound around the horizontal claw shaft 4A, etc. It is constituted by. The anti-winding member 4C includes a cylindrical portion 4Ca formed in a hollow cross shape, a flange portion 4Cb welded to both ends thereof, an insertion portion 4Cc through which the second connecting pin 39 is inserted, and the like. The portion 4Cb is welded to the horizontal claw shaft 4A. And by forming cylindrical part 4Ca of winding prevention member 4C in cross shape, even if winding to cylindrical part 4Ca, such as weeds, occurred, weeds etc. which were wound easily in a cross-shaped concave part In the deep tillage work that makes it difficult to move the machine forward, the tubular portion 4Ca comes into contact with the ground and increases thrust and buoyancy. It is easy to work. The tilling claw 4B is bolted to the outer flange portion 4Cb of the winding preventing member 4C, and thereby rotates integrally with the horizontal claw shaft 4A.
[0035]
As shown in FIGS. 6, 7, and 10, the first connection pin 37 and the second connection pin in the flange portion 4 </ b> Cb of the anti-winding member 4 </ b> C are disposed on the heads of the first connection pin 37 and the second connection pin 39. An engagement rod 41 made of a spring steel material that can be elastically deformed so as to engage with the engagement pin 40 projecting from the lower side in the rotational direction than the head portion of 39 is integrally provided. Thus, the first connecting pin 37 is connected to the left and right output shaft portions 8A and 8B, the relay shaft 34, and the inclined claw shaft 36, and the second connecting pin 39 is connected to the relay shaft 34 and the horizontal claw shaft 4A. It can be easily fixed to the connected state.
[0036]
As shown in FIGS. 6 and 11, a propulsion rotor 42 is mounted on the outer side of the tilling rotor 4 so as to rotate integrally. The propulsion rotor 42 is externally fitted to the horizontal claw shaft 4 </ b> A of the tilling rotor 4. The horizontal shaft 42A, the drum 42B that surrounds the horizontal shaft 42A, the horizontal claw shaft 4A and the propulsion disk 42C welded to the outer end of the drum 42B, and the horizontal shaft 42A are fitted in and engaged with the horizontal shaft 42A. The cap 42D closes the outer opening, and the like. The drum 42B includes a cylindrical portion 42a formed in a hollow cross shape, an inner end of the cylindrical portion 42a, a flange portion 42b welded to the horizontal shaft 42A, and a flange portion 4Cb on the outer end side of the anti-winding member 4C. The connecting pin 42c projecting from the flange portion 42b so as to be connectable to the horizontal shaft 42A, and prevents the weed and the like from being wound around the horizontal shaft 42A. Thrust and buoyancy in deep tillage work are secured. The propulsion disk 42C has a cross shape with a diameter larger than that of the drum 42B, and is formed so as to have a raised portion 42d at each convex portion thereof, thereby ensuring thrust during tillage work and stabilizing the fuselage. It comes to improve the nature. In addition, as shown in FIG. 12, you may employ | adopt the thing formed in the circular shape so that it may have more cut-and-raised part 42d than the thing of a cross shape as the propulsion disk 42C.
[0037]
In the relay shaft 34 of the inclined claw unit U, the outer diameter on the outer end side where the horizontal claw shaft 4 </ b> A of the tilling rotor 4 is fitted is formed to be the same size as the outer diameter of the output shaft 8. In other words, this walk-type field cultivator effectively utilizes the entire walk-type field cultivator in which residual tillage occurs in the field portion below the mission case 2 by directly connecting the cultivation rotor 4 to the output shaft 8. However, the specification has been changed to a full-cut type for plowing the field portion below the mission case 2 with a simple and inexpensive improved configuration in which the inclined claw unit U is interposed between the output shaft 8 and the tilling rotor 4. -ing In addition, with this configuration, by removing the tilting claw unit U for tillage work and the tillage rotor 4 from the output shaft 8, other work devices such as a scraping rotor and a soil cultivating rotor that can be originally mounted can be output. It can be attached to the shaft 8.
[0038]
In the horizontal claw shaft 4 </ b> A of the tilling rotor 4, the outer diameter on the outer end side where the horizontal shaft 42 </ b> A of the propulsion rotor 42 is fitted is the same as the outer diameter on the outer end side of the relay shaft 34 of the inclined claw unit U. Is formed. The propulsion rotor 42 is formed with an insertion portion 42 </ b> E that allows the second connecting pin 39 to be inserted, like the tilling rotor 4. That is, the propulsion rotor 42 is configured to be directly coupled to the inclined claw unit U by the second connecting pin 39, and thereby, with a narrow tillage width performed in a state where only the inclined claw unit U is attached to the output shaft 8. Also in this tilling work, the thrust by the propulsion rotor 42 and the stability of the airframe can be obtained.
[0039]
[Another embodiment]
Hereinafter, other embodiments of the present invention will be listed.
(1) As a walking type tiller, a structure without the transmission 16 or the side clutch mechanism 22 may be provided, and a chain transmission type in which transmission to the output shaft 8 is performed via a rotating chain or the like. It may be configured as described above, and may be configured to further include propulsion wheels.
(2) The position and quantity of the engaged portion 2ca formed on the boss 2c that supports the output shaft 8 can be variously changed.
(3) The engaged portion 2ca may be recessedly formed in the boss 2c that supports the output shaft 8, and the engaging portion 35B may be formed to be engageable with the engaged portion 2ca.
(4) A dedicated oil seal cover may be provided without causing the engaging portion 35B to function as an oil seal cover.
(5) The working device attached to the output shaft 8 may be a scraping rotor, a soil rotator, or the like.
[Brief description of the drawings]
[Fig. 1] Whole side view of walking type tiller [Fig. 2] Transverse plan view of the main part showing the configuration of the planetary speed reducer [Fig. 3] Longitudinal side view of the main part showing the transmission configuration of the walking type tiller [Fig. 4] Longitudinal rear view of the main part showing the straight state of the side clutch mechanism [FIG. 5] Vertical rear view of the main part showing the turning state of the side clutch mechanism [FIG. 6] Longitudinal rear view of the main part showing the configuration of the inclined claw unit [Fig. 7] Side view of the inclined claw shaft [Fig. 8] Plan view of the inclined claw shaft [Fig. 9] Vertical side view of the main part showing the detent structure of the inclined bolster [Fig. 10] [Fig. 11] Side view of the propulsion rotor [Fig. 12] Side view showing another configuration of the propulsion rotor [Explanation of symbols]
2c boss 2ca engaged portion 4 tilling rotor 8 output shaft 34 relay shaft 35 inclined bracket 35A inclined boss 35B engaging portion 36 inclined claw shaft
36B Tillage Claw 36C Winding Prevention Member 36D Winding Prevention Member 37 Connection Pin 38 Oil Seal U Inclination Claw Unit

Claims (3)

A relay shaft in a horizontal position, an inclined bracket fitted with the relay shaft in a state allowing its rotation and an inclined boss in a downwardly inclined posture, and externally attached to the inclined boss in a state of rotating integrally with the relay shaft. An inclined claw unit is constructed from the fitted inclined claw shaft,
The relay shaft can be connected to the output shaft for tillage, and the tillage rotor can be connected to the outer end side thereof,
The tilt bracket can be connected to the machine body in a non-rotatable manner, and the anti-rotation connection is formed in an engaged part formed on a boss on the machine body side that supports the output shaft, and an engagement part formed in the tilt bracket. Configured to be engaged with
The inclined claw unit is attached to the output shaft by a single connecting pin, and as a result of the attachment, the relay shaft and the inclined claw shaft rotate integrally with the output shaft, and the inclined bracket is mounted on the body side. Configured to maintain a non-rotating connection state ,
There is no cultivating claw provided on the inclined claw shaft and a connecting tool for attaching the cultivating claw to the inclined claw shaft in the attachment / detachment direction of the connecting pin in the inclined claw unit. Thus, a full-cut walking type tiller that is displaced in the rotational direction of the inclined claw unit with respect to the connector .   The full-cut walking type tiller according to claim 1, wherein the engaging portion is formed so as to cover an oil seal interposed between the output shaft and the boss.   The full-cut walking type tiller according to claim 1 or 2, wherein a winding prevention member is provided on the inclined claw shaft.

Images