JP2013066485A - Walking-type mower - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a walking-type mower having a simple structure and allowing a mowing operation to be suitably carried out as a traveling machine body is advanced or retreated.SOLUTION: A traveling machine body 1 includes a motor unit E, a traveling device that is rotated by power from the motor unit E, and a cutting blade 10. The cutting blade 10 is supported against the lower portion of the motor unit E in such a manner as to freely rotate about a vertical axis P2. The motor unit E and the cutting blade 10 are supported against the traveling machine body 1 in such a manner as to be capable of swinging about a horizontal axis P1. With the traveling device grounded on a grounding surface, the motor unit E and the cutting blade 10 are supported against the traveling machine body 1 without the cutting blade 10 being grounded on the grounding surface. An inclined attitude varying mechanism is provided for varying the attitudes of the motor unit E and the cutting blade 10 between a forwardly downwardly inclined attitude in which the front side of the cutting blade 10 swings downward and a backwardly downwardly inclined attitude in which the rear side of the cutting blade 10 swings downward.

Description

  The present invention relates to a walking mower having a traveling machine body that includes a driving unit, a traveling device that rotates by power from the driving unit, and a cutting blade.

  As a conventional technique, for example, as disclosed in Patent Document 1, an engine (5 in FIG. 1 of Patent Document 1) is mounted on a traveling machine body having traveling wheels (4 in FIG. 1 of Patent Document 1). A walking type mower having a cutting blade (2 in FIG. 1 of Patent Document 1) that rotates by power from the engine is known.

Japanese Patent Laid-Open No. 2007-53991 (see FIGS. 1, 2, 13, and 14)

  In the walking type mower of Patent Document 1, the base (66 in FIG. 13 of Patent Document 1) and the blade piece (67 in FIG. 13 of Patent Document 1) constituting the cutting blade are driven so as to be substantially horizontal with the ground. When a cutting blade is attached to the lower part of the case (9 in FIG. 13 of Patent Document 1) and the walking type grass mower is advanced, the grass introduced from the front is cut off at the front part of the cutting blade, and the walking type grass cutting machine. When the machine is moved backward, the grass introduced from behind is cut off at the rear part of the cutting blade.

Therefore, although the part of the cutting blade that actually cuts the grass is the front part or the rear part of the cutting blade, even when the walking type grass mower is advanced, even when the walking type grass mower is moved backward, The lower surface side of the cutting blade was located at a position close to the ground over almost the entire area, and the grass growing on the ground after being cut through the lower side of the cutting blade was likely to become a resistance to rotate the cutting blade. . As a result, the load on the engine due to the driving of the cutting blade is increased, and there is room for improvement from the viewpoint of reducing the size of the engine and reducing the weight of the walking type mower.
The present invention has a simple structure for a walk-type grass mower capable of saving the power to rotate the cutting blade while enabling the cutting operation by moving the traveling body forward and the cutting operation by moving the traveling body backward. It aims to be realized with.

[I]
(Constitution)
A first feature of the present invention is a walking mower having a traveling machine body provided with a prime mover, a running device that is rotated by power from the prime mover, and a cutting blade. is there.
On the traveling machine body, the cutting blade is supported so as to be rotatable around a vertical axis and swingable around a horizontal axis,
When the traveling machine body is moved forward, the posture is changed to a forward downward inclined posture in which the front side of the cutting blade swings downward, and when the traveling vehicle body is moved backward, the rear side of the cutting blade swings downward to a downward lowered inclined posture. An inclined posture changing mechanism for changing the posture is provided.

(Function)
According to the first feature of the present invention, the grass introduced from the front by the front part (rear part) of the cutting blade whose posture has been changed to the forward downward inclination posture (rear downward inclination posture) by moving the traveling body forward (reverse). Can be reaped. In this case, even if the cutting blade is in a forward-falling inclination posture (rear-falling inclination posture), it is the front side (rear side) of the cutting blade that cuts the grass. it can. In the front-falling inclination posture (rear-falling inclination posture), since the rear side (front side) of the cutting blade is separated upward, the grass passing under the cutting blade is less likely to become a resistance to rotate the cutting blade. It is possible to reduce the load on the prime mover driven by the cutting blade. As a result, it is possible to set the output of the driving unit that drives the cutting blade to be small while rotating the cutting blade while enabling the cutting operation by moving the traveling vehicle forward and the cutting operation by moving the traveling aircraft backward. You can save power to make.

  According to the first feature of the present invention, since the cutting blade is supported by the traveling machine body so as to be swingable around the left and right axis, the cutting blade is tilted forward by swinging the cutting blade with respect to the traveling machine body. The posture and the downwardly inclined posture can be easily displayed. As a result, the cutting blade can be easily switched between the forward and downward tilt postures, and the structure of the tilt posture changing mechanism can be simplified.

(Effect of the invention)
According to the 1st characteristic of this invention, while being able to achieve size reduction of a drive part and weight reduction of a walk-type mower, the manufacturing cost of a walk-type mower can be reduced.

[II]
(Constitution)
The second feature of the present invention resides in the following configuration in the walking mower of the first feature of the present invention.
While supporting the cutting blade at the lower part of the driving part so as to be rotatable around a vertical axis,
The tilting posture changing mechanism is configured by supporting the driving unit on the traveling machine body so as to be swingable around a left and right axis.

(Function)
According to the second feature of the present invention, the “action” described in the preceding item [I] is provided in the same manner as the first feature of the present invention, and in addition to this, the following “action” is provided.
According to the second feature of the present invention, by swinging the driving part around the left and right axis with respect to the traveling machine body, the cutting blade swings around the left and right axis with respect to the traveling machine body, It is possible to easily show the forward and downward inclined postures of the cutting blade. For example, if only the cutting blade is configured to swing around the left and right axis, the connection structure between the cutting blade and the driving part may be complicated, but the driving part and the cutting blade are integrated around the left and right axis. By swinging in the direction, it is possible to prevent the connection structure between the cutting blade and the prime mover from becoming complicated. As a result, the cutting blade can be switched between the forward and downward tilt postures more easily, and the structure of the tilt posture changing mechanism can be further simplified.

(Effect of the invention)
According to the second feature of the present invention, the “effect of the invention” described in the preceding item [I] is provided in the same manner as the first feature of the present invention. In addition, the following “effect of the invention” is provided. ing.
According to the second feature of the present invention, it is possible to further reduce the weight of the walking mower, and to further reduce the manufacturing cost of the walking mower.

[III]
(Constitution)
The third feature of the present invention resides in the following configuration in the walking mower of the second feature of the present invention.
Extending a concentric drive shaft and a swinging support shaft from the left and right sides of the prime mover in the left-right direction, and transmitting power from the prime mover to the travel device via the drive shaft,
The tilt posture changing mechanism is configured by supporting the drive shaft and the swing support shaft on the traveling machine body so as to be rotatable around a left and right axis.

(Function)
According to the third feature of the present invention, the “action” described in the preceding item [II] is provided in the same manner as the second feature of the present invention. In addition, the following “action” is provided.
According to the third feature of the present invention, when the traveling shaft is moved forward (reverse) by rotating the drive shaft by the power from the prime mover, the force in the direction opposite to the direction in which the drive shaft rotates is determined by the law of action and reaction of the force. Acts on the prime mover, the prime mover and the cutting blade swing together, and the posture is changed to a forward downward tilting posture (backward downward tilting posture) in which the front side (rear side) of the cutting blade swings downward. As a result, it is possible to automatically change the orientation of the cutting blade to the forward and downward tilting posture (backward downward tilting posture) by effectively utilizing the inertial force generated by driving the traveling device, and to change the traveling direction of the traveling aircraft By doing so, it is possible to automatically switch between the forward and downward tilt posture.

  Specifically, for example, as shown in FIG. 13, when the traveling machine body is advanced and the drive shaft (7a in FIG. 13) rotates clockwise around the left and right axis (P1 in FIG. 13), the action and reaction of the force According to the law, a counterclockwise force around the left and right axial centers of the drive shaft acts on the driving portion (E in FIG. 13), and the driving portion and the cutting blade (10 in FIG. 13) integrally swing forward. The posture is changed to a forward downward inclined posture in which the front side of the cutting blade swings downward. Further, for example, as shown in FIG. 14, when the traveling machine body is moved backward and the drive shaft is rotated counterclockwise around the left and right axis, a clockwise action around the left and right axis of the drive shaft is obtained according to the law of action and reaction of force. The force acts on the prime mover (E in FIG. 14), and the prime mover and the cutting blade (10 in FIG. 14) integrally swing back, and the rear side of the cutting blade (10 in FIG. 14) swings downward. The posture is changed to a rear-falling inclined posture.

(Effect of the invention)
According to the third feature of the present invention, the “effect of the invention” described in the preceding item [II] is provided in the same manner as the second feature of the present invention. In addition, the following “effect of the invention” is provided. ing.
According to the third feature of the present invention, it is possible to easily and quickly switch between the forward and downward tilting postures of the cutting blade, improve the workability of the cutting operation, and further simplify the structure of the tilting posture changing mechanism. it can.

[IV]
(Constitution)
A fourth feature of the present invention resides in the following configuration in the walking mower according to any one of the first to third features of the present invention.
An inclination angle adjusting mechanism capable of changing and adjusting a front lower inclination angle of the cutting blade in the front lower inclination attitude or a rear lower inclination angle of the cutting blade in the rear lower inclination attitude.

(Function)
According to the fourth feature of the present invention, the “action” described in the preceding paragraphs [I] to [III] is provided in the same manner as any one of the first feature to the third feature of the present invention. The following “actions” are provided.
According to the fourth feature of the present invention, the height of the cutting blade can be changed by changing the front downward inclination angle or the rear downward inclination angle of the cutting blade by the inclination angle adjusting mechanism, and according to the length of the grass. By adjusting the tilt angle adjusting mechanism, the grass can be cut long or short. As a result, the mechanism for changing and adjusting the grass cutting height can be simplified, and the number of parts of the mechanism for changing and adjusting the grass cutting height can be reduced.

(Effect of the invention)
According to the fourth feature of the present invention, as in any one of the first feature to the third feature of the present invention, the “effect of the invention” described in the preceding items [I] to [III] is provided. In addition, the following “effects of the invention” are provided.
According to the 4th characteristic of this invention, the manufacturing cost of a walk-type grass-cutting machine can be restrained low, configuring so that the cutting height of grass can be changed.

Overall left side view of walking mower Overall plan view of walking type mower Longitudinal left side view of traveling aircraft Cross-sectional plan view of traveling aircraft Longitudinal rear view of traveling aircraft A longitudinal rear view for explaining the support structure of the front and rear wheels Vertical side view explaining the structure of the movable shatterproof cover Cross-sectional plan view explaining the structure of the cutting blade Transmission system diagram of walking type mower Longitudinal rear view showing the power transmission structure of a walking mower Cross-sectional plan view showing the transmission structure of a walking type mower Perspective view of cutting blade clutch Schematic right side view explaining the state of inclination of the cutting blade when it is moved forward Schematic right side view explaining the state of inclination of the cutting blade when it is moved backward

[Walking mower overall configuration]
Based on FIGS. 1-6, the whole structure of a walk-type mower is demonstrated. 1 and 2 show an overall left side view and an overall plan view of the walking mower, respectively, and FIGS. 3 to 5 show a longitudinal left side view, a transverse plan view, and a longitudinal rear view of the traveling machine body 1, respectively. . FIG. 6 is a longitudinal rear view for explaining the support structure of the front wheel 5 and the rear wheel 6.

  As shown in FIGS. 1 and 2, a front axle 3 and a rear axle 4 are pivotally supported on a body frame 2 mounted on the traveling body 1, and left and right end portions of the front axle 3 and the rear axle 4 are supported. The front wheels 5 and 5 and the rear wheels 6 and 6 (corresponding to traveling devices) made of sheet metal are fixed to each. A transmission case 7 is supported on the upper part of the machine body frame 2 so as to be swingable around a left and right axis P1, and an engine 8 integrally formed with a fuel tank 8a is interlocked and connected to the upper part of the transmission case 7. Thus, the driving part E is configured. The engine 8 is equipped with a recoil type starter 8b, and the engine 8 can be driven by the starter 8b.

  A chain transmission mechanism 9 is disposed on the right side of the traveling machine body 1, and the power from the engine 8 is transmitted to the chain transmission mechanism 9 via a transmission path in the transmission case 7 so that the front axle 3 and the rear axle are transmitted. 4 rotates, and the left and right front wheels 5 and rear wheels 6 rotate. A cutting blade 10 is attached to the lower part of the transmission case 7, and the power from the engine 8 is transmitted to the cutting blade 10 via a transmission path in the transmission case 7, so that the cutting blade 10 rotates and cuts grass. It is configured to be able to.

  As shown in FIGS. 4 and 5, a U-shaped frame 18 is fixed to the upper part of the body frame 2 in a plan view, and an end of the frame 18 extending leftward from the body frame 2. The support shaft 19 is supported by the portion so as to be rotatable around a vertical axis. A bracket 20 is supported on the upper end portion of the support shaft 19 so as to be rotatable around a lateral axis, and a pipe-like steering handle 21 is fixed to the bracket 20.

  As shown in FIG. 1 and FIG. 2, the steering handle 21 is swingable about the vertical axis and is set in advance by the action of the first lock mechanism 22 provided between the steering handle 21 and the frame 18. It is configured so that it can be selectively fixed and held at a plurality of swing positions around the vertical axis, and is swingable about the horizontal axis, and is provided between the frame 18 and a second frame. By the action of the lock mechanism 23, the lock mechanism 23 can be selectively fixed and held at a plurality of swing positions around a preset lateral axis.

  The extending end of the steering handle 21 is equipped with a grip 21a. The first release that enables the grip 21a to be unlocked by the first lock mechanism 22 that is spring-biased in a locked state. The lever 24 and the second release lever 25 that enables the unlocking operation of the second lock mechanism 23 spring-biased in the locked state are attached, and are linked to the first and second lock mechanisms 22 and 23, respectively. Yes.

  A main clutch lever 21b is mounted on the extending end of the steering handle 21 so as to be swingable up and down around a lateral axis, and is linked to a main clutch 63, which will be described later, to rotate the cutting blade 10. It is comprised so that a stop and the traveling body 1 can be stopped.

  A forward / reverse switching lever 26 that can be switched to a forward position, a neutral position, and a backward position is supported at the rear end of the steering handle 21 so as to be swingable to the left and right around a vertical axis. An operation arm 85, which will be described later, is linked to the lever 26 so that the walking type mower can be switched forward, stop (neutral), and reverse by operating the forward / reverse switching lever 26.

  As shown in FIGS. 3, 4, and 6, the fuselage frame 2 is provided across right and left main frames 31, 32 that are long in the front-rear direction and front ends of the right and left main frames 31, 32. A front frame 33 and a rear frame 34 provided over rear ends of the right and left main frames 31 and 32 are provided.

  The front and rear frames 33 and 34 are constituted by cylindrical members, and the front axle 3 facing left and right is rotatably fitted to the front frame 33 via left and right bearing members 37. A left and right rear axle 4 is rotatably fitted in the rear frame 34 via left and right bearing members 38.

  A front rod 35 that protects the front part of the traveling machine body 1 is mounted over the front ends of the right and left main frames 31 and 32, and the traveling machine body 1 is installed over the rear ends of the right and left main frames 31 and 32. A rear rod 36 for protecting the rear portion is mounted.

  As shown in FIGS. 3 to 5, a drive shaft 7 a extends rightward from the transmission case 7, and this drive shaft 7 a is rotatably supported by a right main frame 31 via a bearing member 39. ing. A swing support shaft 7b concentric with the drive shaft 7a extends from the transmission case 7 to the left. The swing support shaft 7b extends to the left main frame 32 via a bearing member 40 and has a left-right axis. It is rotatably supported around P1. As a result, the transmission case 7, the engine 8 attached to the transmission case 7, the cutting blade 10 and the like can be supported integrally with the body frame 2 so as to be able to swing back and forth around the axis P1 in the left-right direction.

  The positions of the driving shaft 7a and the swinging support shaft 7b in the front-rear direction in the lateral direction of the axial center P1 are the transmission case 7, the engine 8 and the cutting blade 10 supported by the drive shaft 7a and the swinging support shaft 7b. When the driving shaft 7a is stopped and no inertial force is applied to the transmission case 7 or the like, the cutting blade 10 is substantially horizontal with the ground. In a state where the drive shaft 7a is rotated and the inertial force acts on the transmission case 7 and the like, the inertial force generated by rotating the drive shaft 7a by the force around the axis P1 due to the weight of the transmission case 7 and the like is maintained. This is configured so that the cutting blade 10 is changed in posture to a front-falling inclination posture and a rear-falling inclination posture (see FIGS. 13 and 14).

  As shown in FIGS. 3 to 6, a chain transmission mechanism 9 is provided on the right outer side of the right main frame 31. The chain transmission mechanism 9 includes a drive sprocket 41 linked to the right outer end of the drive shaft 7a, a front sprocket 42 linked to the right outer end of the front axle 3, and a right outer portion of the rear axle 4. The rear sprocket 43 linked to the end, the tension sprocket 44 disposed on the top of the drive sprocket 41, the drive sprocket 41, the front and rear sprockets 42 and 43, and the tension sprocket 44 And a transmission chain 45 provided.

  A right side surface of the right main frame 31 is provided with a chain cover 46 that is divided into left and right parts. The left chain cover 46a is fixed to the right main frame 31, and the left chain cover 46a is attached to the right outer side. The chain transmission mechanism 9 can be covered with the chain cover 46 by tightening and fixing the right chain cover 46b from the side.

  A tension sprocket 44 is supported at the upper part of the front and rear central part of the left chain cover 46a so as to be rotatable about a left and right axis. The tension sprocket 44 is attached to the left chain cover 46a so that its position can be changed in the vertical direction. The tension sprocket 44 is configured so that the tension of the transmission chain 45 can be adjusted by adjusting the position of the tension sprocket 44 in the vertical direction. .

  A cover 50 is detachably attached to the front and rear center portion of the right chain cover 46b from the right outer side, and the inside of the chain cover 46 can be inspected by removing the cover 50.

  Left and right front wheels 5 and 5 and rear wheels 6 and 6 are externally fitted and inserted into the left and right ends of the front axle 3 and the rear axle 4 from the laterally outer side, so that the front axle 3 and the rear axle 4 rotate together. It is fixed so that it can move. When the power from the engine 8 is transmitted to the drive shaft 7a through the transmission case 7 and the front axle 3 and the rear axle 4 rotate through the chain transmission mechanism 9, the front wheels 5 and the rear wheels 6 rotate, and walking type mowing. The machine is configured to move forward or backward.

  As described above, the drive shaft 7a and the swing support shaft 7b extending from the transmission case 7 are supported on the body frame 2 of the traveling machine body 1 so as to be swingable around the axis P1 in the left-right direction. When the traveling machine body 1 is advanced by transmitting power to the drive shaft 7a through the transmission case 7, and rotating the front wheels 5 and the rear wheels 6 through the chain transmission mechanism 9 by the power from the drive shaft 7a, the cutting blade An inclination posture changing mechanism in which the posture is changed to a forward downward inclined posture in which the front side of 10 is swung downward, and the posture is changed to a downward inclined posture after the rear side of the cutting blade 10 is swung downward when the traveling machine body 1 is moved backward. (See FIGS. 13 and 14).

[Detailed structure of the cover]
Based on FIGS. 4-7, the detailed structure of the cover with which the traveling body 1 is mounted | worn is demonstrated. FIG. 7 shows a longitudinal side view of the structure of the movable scattering prevention cover 54 as viewed from the inside of the machine body.

  As shown in FIGS. 4 and 5, left and right upper covers 51 are fixed to the lower surfaces of the front and rear central portions of the right and left main frames 31, 32, and left and right upper covers 51 are prevented from fixing left and right fixed scattering. The cover 52 is fixed. The gap between the lower end of the left fixed anti-scatter cover 52 and the ground is set wider than the gap between the lower end of the right anti-scatter cover 52 and the ground, and the left anti-scatter cover 52 will be described later. In cooperation with the movable scattering prevention cover 54, it is configured to prevent scattering of the cut grass to the left side.

  As shown in FIGS. 5 and 7, front and rear brackets 53 extend downward from the frame 18, and a movable scattering prevention cover 54 is attached to the front and rear brackets 53. The movable scattering prevention cover 54 has long front and rear long holes 54A formed in the vertical direction, and front and rear pins 53A extending leftward from the front and rear brackets 53 are communicated with the front and rear long holes 54A. . A spring mounting portion 54 a that protrudes inward is provided on the upper part of the movable scattering prevention cover 54, and an elastic spring 55 is mounted across the spring mounting portion 54 a and the front and rear brackets 53.

  The lower part of the front end portion of the movable scattering prevention cover 54 is formed with a front inclined portion 54b that is notched upward in the side view, and the rear lower portion of the movable scattering prevention cover 54 is rearward in the side view. A rear inclined portion 54c cut out upward is formed. As a result, for example, when an ambulatory mower is moved forward and an obstacle such as a stone from the front left side comes into contact with the movable scattering prevention cover 54, the biasing force of the elastic spring 55 is caused by the elongated hole 54A formed in the movable scattering prevention cover 54. The movable scattering prevention cover 54 moves upward against this. On the contrary, when the walking type mower is moved backward and an obstacle such as a stone comes into contact with the movable scattering prevention cover 54 from the left rear side, the urging force of the elastic spring 55 is resisted by the elongated hole 54A formed in the movable scattering prevention cover 54. Then, the movable scattering prevention cover 54 moves upward.

  As shown in FIGS. 4 and 5, the front part and the rear part of the movable scattering prevention cover 54 are arranged along the outer surfaces of the left front wheel 5 and the rear wheel 6, and the front end part and the rear end part are inward, respectively. The front end portion and the rear end portion bent inward are formed so as to overlap the front wheel 5 and the rear wheel 6 in plan view. Further, the gap between the lower end of the movable scattering prevention cover 54 and the ground is set to be substantially the same as the gap between the lower end of the right fixed scattering prevention cover 52 and the ground. Thereby, the clearance between the lower end of the movable scattering prevention cover 54 and the ground, and the clearance between the movable scattering prevention cover 54 and the front wheel 5 and the rear wheel 6 can be set small, and scattering of the cut grass to the left side can be effectively performed. Can be prevented.

  By configuring the movable scattering prevention cover 54 as described above, normally, the movable scattering prevention cover 54 is urged downward by the urging force of the elastic spring 55 to widely move between the front wheel 5 and the rear wheel 6. The anti-scattering cover 54 can be covered from the side, and when it comes into contact with an obstacle, the movable anti-scattering cover 54 moves upward against the urging force of the elastic spring 55 to damage the movable anti-scattering cover 54. Can be prevented. The movable scattering prevention cover 54 may be provided on the right side of the traveling machine body 1, and the movable scattering prevention cover 54 may be provided on both the left and right sides of the traveling machine body 1.

  As shown in FIGS. 3 and 6, the front frame 33 provided across the right and left main frames 31, 32 has a rubber front scattering prevention member 56 that covers the space between the left and right front wheels 5. A rear frame 34 that is swingably mounted back and forth around the axis in the left-right direction and that is provided over the right and left main frames 31, 32 is made of rubber that covers the space between the left and right rear wheels 6. The rear scattering prevention member 57 is mounted so as to be swingable back and forth around the axis in the left-right direction. The left and right end portions of the front and rear scattering prevention covers 56 and 57 are shaped so as to enter the inside of the front wheel 5 and the rear wheel 6, respectively, thereby effectively scattering the cutting grass forward and backward. Can be prevented.

  As shown in FIGS. 4 and 6, the body frame 2 is covered from above by front and rear upper covers 58 that are divided into front and rear parts. The center part of the front and rear upper covers 58 is formed in a shape bulging upward, the outer peripheral part is formed in a horizontal shape, and the left and right side parts formed in the horizontal shape of the front and rear upper cover 58 are right and right. It is fastened and fixed at a plurality of locations on the upper surface side of the left main frames 31 and 32.

[Detailed structure of the cutting blade]
Based on FIG.5 and FIG.8, the detailed structure of the cutting blade 10 is demonstrated. FIG. 8 is a cross-sectional plan view illustrating the structure of the cutting blade 10.

  As shown in FIGS. 5 and 8, the cutting blade 10 includes a boss member 11 that attaches the cutting blade 10 to the lower portion of the transmission case 7, a rotating disk 12 fixed to the boss member 11, and a rotating disk 12. And a plurality of cutting blade bodies 13 rotatably supported on the outer peripheral portion, and a plurality of diffusion blades 14 fixed to the upper surface side of the rotating disk 12.

  The rotating disk 12 is formed in a downward dish shape that is inclined outward and downward so that the distance from the ground gradually decreases outward from the fixing portion with the boss member 11, and the ground and A substantially horizontal horizontal portion 12a is formed. The cutting blade body 13 is composed of an upper cutting blade body 13a formed into a shape inclined obliquely outward and upward, and a lower cutting blade body 13b formed into a shape inclined obliquely outward and downward. The upper cutting blade body 13a and the lower cutting blade body 13b are alternately supported by the pins 15 at an equal pitch of about 90 degrees at a plurality of positions on the horizontal portion 12a on the outer peripheral portion of the rotating disk 12. Has been.

  The diffusion blades 14 are shaped so that the upper end portion thereof is inclined obliquely upward and upward so that the area of the blades gradually increases toward the outer side, and the cutting blade bodies adjacent to each other from the axis P2 Thirteen intermediate positions are arranged radially at an equal pitch of about 90 degrees.

  A cutting blade cover 16 is attached to the lower part of the transmission case 7, and the cutting blade cover 16 prevents the cutting grass from entering the rotation center side so that the cutting grass can be prevented from being wound around the rotation center. It is configured.

[Transmission structure of walking type mower]
Based on FIGS. 9-12, the transmission structure of a walk-type mower is demonstrated. FIG. 9 shows a transmission system diagram of the walking mower, and FIGS. 10 and 11 show a longitudinal rear view and a transverse plan view of the transmission structure of the walking mower, respectively. FIG. 12 is a perspective view of the cutting blade clutch 68.

  As shown in FIGS. 9 to 11, a vertical input shaft 62 is rotatably supported on the upper portion of the transmission case 7 via a pair of bearings 61, and the upper end portion of the input shaft 62 is connected to the transmission case 7. The main shaft 63 is connected to an output shaft 8c of the engine 8 fixed to the upper portion. A transmission gear 64 is connected to a lower portion of the input shaft 62 so as to be integrally rotatable. The transmission gear 64 is engaged with a transmission gear 72 that is interlocked and connected to an upper transmission shaft 65 described later.

  An upper transmission shaft 65 and a lower transmission shaft 66 that are concentrically disposed around a vertical axis P2 of the transmission case 7 are rotatably supported via a plurality of bearings 67. A cutting blade clutch 68 is mounted across the lower transmission shaft 66. The boss member 11 of the cutting blade 10 is fastened and fixed to the lower end portion of the lower transmission shaft 66 from below, and when the cutting blade clutch 68 is operated to the ingress side, the power from the engine 8 is input to the input shaft 62 and the upper transmission. The cutting blade 10 is configured to rotate by being transmitted to the lower transmission shaft 66 via the shaft 65 and the cutting blade clutch 68.

As shown in FIGS. 10 and 12, the cutting blade clutch 68 can rotate integrally with the upper clutch 69 linked to the upper transmission shaft 65 and the lower transmission shaft 66 and can slide up and down by a spline structure. The upper clutch 69 and the lower clutch 70 are formed with engaging pieces 69a and 70a that are engaged with each other.

  An elastic spring 68a that urges the lower clutch 70 upward is mounted across the lower surface side of the lower clutch 70 and the upper surface side of the bearing 67, and the cutting blade clutch 68 is urged toward the entry side by the elastic spring 68a. It is comprised so that.

  The engaging pieces 69a and 70a are formed with inclined portions 69b and 70b that are inclined obliquely. When power from the engine 8 is transmitted to the lower transmission shaft 66 via the upper transmission shaft 65, the upper clutch The engagement piece 69 a of 69 and the engagement piece 70 a of the lower clutch 70 mesh with each other, and the power from the engine 8 is transmitted to the lower transmission shaft 66.

  For example, when the engine 8 is stopped and the rotation of the upper transmission shaft 65 is stopped, the cutting blade 10 is rotated by the inertial force, and the inertial force from the cutting blade 10 is transmitted from the lower transmission shaft 66 to the upper transmission shaft 65. As a result, the lower clutch 70 is rotated relative to the upper clutch 69 by the inclined portions 69b and 70b of the engagement pieces 69a and 70a, and the inertial force from the lower transmission shaft 66 is transmitted to the upper transmission shaft 65. Is cut off. When the rotation of the cutting blade 10 due to the inertial force stops, the lower clutch 70 is operated upward by the biasing force of the elastic spring 68a, and the cutting blade clutch 68 is operated on the entry side.

  As a result, it is possible to prevent the inertial force of the cutting blade 10 from rotating along the transmission upstream side (the engine 8 side and the drive shaft 7b side) (for example, the front wheel 5 and the rear wheel 6 are moved by the inertial force of the cutting blade 10). In addition, for example, a brake device (not shown) that forcibly brakes the rotation of the cutting blade 10 is provided on the transmission upstream side of the cutting blade 10 (for example, the upper transmission shaft 65 or the lower transmission shaft 66), and the engine 8 Compared to a configuration in which the inertial force due to the rotation of the cutting blade 10 when it is stopped is not transmitted to the transmission upstream side, the mechanism for suppressing the transmission of the inertial force from the cutting blade 10 to the transmission upstream side is simplified. Manufacturing costs can be reduced.

  The lower clutch 70 is formed with a shift groove 70c in the outer periphery of the lower portion of the lower clutch 70 so as to function as a shift member of the cutting blade clutch 68. When the operating portion 71a of the shift lever 71 supported so as to be swingable to the left and right is engaged and the lever main body 71b of the shift lever 71 is operated to swing, the lower clutch 70 slides up and down and the cutting blade clutch 68 is disconnected. It is configured to be able to contact.

As shown in FIGS. 9 to 11, transmission gears 72 and 73 are interlocked to the upper transmission shaft 65, and the transmission gear 72 is engaged with a transmission gear 64 fixed to the input shaft 62. A transmission gear 75 is interlocked and connected to a transmission shaft 74 that is supported by the transmission case 7 in a freely rotating manner, and this transmission gear 75 is engaged with a transmission gear 73 that is interlocked and connected to the upper transmission shaft 65. The power from the upper transmission shaft 65 facing up and down is changed by 90 degrees and transmitted to the transmission shaft 74 facing front and rear. A transmission gear 76 is interlocked and connected to the transmission shaft 74, and this transmission gear 76 is engaged with a transmission gear 78 disposed on the lower right side of the transmission shaft 74 and interlocked and connected to the transmission shaft 77.

  A bevel gear 79 is interlocked to the transmission shaft 77, and the bevel gear 79 is engaged with a forward-bevel gear 80 and a backward-bevel gear 81 that are externally fitted to the left-right drive shaft 7a. The drive shaft 7a is supported by the transmission case 7 via a bearing 83 so as to be rotatable about a left and right axis P1, and forward and reverse bevel gears 80 and 81 are rotatable on the drive shaft 7a. The shift member 82 is externally fitted between the forward-bevel gear 80 and the backward-bevel gear 81 so as to be slidable in the left-right direction and to be rotatable integrally with the drive shaft 7a.

  In the transmission case 7, an operation shaft 84 is supported so as to be rotatable around a vertical axis, and an operation arm 85 and upper and lower operation members 86 are connected to an upper end portion and a lower end portion of the operation shaft 84. Yes. A shift groove 82a is formed on the outer periphery of the shift member 82, and an operation member 86 connected to the operation shaft 84 is engaged with the shift groove 82a. When the operation arm 85 is swung back and forth, the shift member 82 slides in the left-right direction and meshes with the forward-bevel gear 80 or the backward-bevel gear 81 so that the traveling machine body 1 can be switched between forward, stop (neutral), and reverse. It is configured. Thus, the forward / reverse clutch 87 is constituted by the bevel gear 79, the forward bevel gear 80, the reverse bevel gear, the shift member 82, and the like.

  As shown in FIGS. 1 and 2, the operating arm 85 is linked to the forward / reverse switching lever 26 provided on the steering handle 21, and when the forward / backward switching lever 26 is operated to swing forward (left side), The operating arm 85 is swung backward, the shift member 82 is engaged with the forward bevel gear 80, the forward / reverse clutch 87 is operated to enter the forward side, and the power from the bevel gear 79 is transmitted via the forward bevel gear 80 and the shift member 82. Is transmitted to the drive shaft 7a, and the drive shaft 7a is driven to rotate forward. On the other hand, when the forward / reverse switching lever 21 is swung to the reverse side (right side), the operation arm 85 is swung forward, the shift member 82 is engaged with the reverse bevel gear 81, and the forward / reverse clutch 87 enters the reverse side. By being operated, the power from the bevel gear 79 is transmitted to the drive shaft 7a via the reverse bevel gear 81 and the shift member 82, and the drive shaft 7a is driven to rotate in reverse.

  As shown in FIGS. 9 to 11, the drive sprocket 41 of the chain transmission mechanism 9 is interlocked with the right end portion of the drive shaft 7 a, and the power from the drive shaft 7 a is forwarded via the chain transmission mechanism 9. The transmission is transmitted to the axle 3 and the rear axle 4 so that the front wheels 5 and the rear wheels 6 are rotated forward and backward, and the traveling machine body 1 moves forward or backward.

[Detailed structure of cutting height adjustment mechanism]
Based on FIG.3 and FIG.4, the detailed structure of the cutting height adjustment mechanism 90 (equivalent to an inclination angle adjustment mechanism) is demonstrated. As shown in FIGS. 3 and 4, the connecting rod spans between a bracket 91 clamped and fixed to the upper surface of the rear portion of the left main frame 32 and a plate-shaped bracket 92 clamped and fixed to the left side of the transmission case 7. The cutting height adjusting mechanism 90 that regulates the lower limit range of the cutting height is configured by linking 93.

  The bracket 91 is formed by bending a plate material into an L shape, and three adjustment holes 91A, 91B, 91C are processed in a portion extending upward from a portion fixed to the left main frame 32. Yes. The upper adjustment hole 91A is formed into a round hole, and the center adjustment hole 91B and the lower adjustment hole 91C are each formed into a long long hole in the front and rear direction. The lengths of the elongated holes of the adjustment holes 91B and 91C are set so as to gradually increase so that the cutting heights H1, H2, and H3, which will be described later, increase at substantially equal intervals.

  The front end portion and the rear end portion of the linkage rod 93 are formed to be bent inward and outward, respectively, and the front end portion of the linkage rod 93 is linked to the left and right through holes in the upper portion of the bracket 92. By connecting the rear end portion of the linkage rod 93 to any one of the adjustment holes 91A, 91B, 91C of the bracket 91 with the pin 94, the swing range of the transmission case 7 and the like around the left-right axis P1 It is comprised so that the upper limit of can be regulated.

  Even if the rear end portion of the linkage rod 93 is linked to the adjustment hole 91A, the swinging of the transmission case 7 around the left and right axis P1 is restricted, and the cutting blade 10 is rotated by driving the engine 8. The height of the lower end portion of the cutting blade 10 remains H1 and does not change.

  When the rear end portion of the linkage rod 93 is linked to the adjustment hole 91B, the movement of the rear end portion of the linkage rod 93 is allowed in the range of the elongated hole of the adjustment hole 91B, and the transmission case 7 around the axis P1 in the left-right direction. Is allowed in the range of the elongated hole of the adjustment hole 91B. For example, when the engine 8 is driven and the forward / reverse switching lever 26 is operated forward, the cutting blade 10 connected to the lower end of the transmission case 7 is allowed in the adjustment hole 91B from the height H1 substantially horizontal to the ground. Tilt in range. And the rear-end part of the linkage rod 93 contacts the front-end | tip of the adjustment hole 91B, the height of the lower end part of the cutting blade 10 is automatically changed into height H2, and the height H2 is maintained. .

  When the rear end portion of the linkage rod 93 is linked to the adjustment hole 91C, the movement of the rear end portion of the linkage rod 93 is allowed in the range of the long hole of the adjustment hole 91C, and the transmission case 7 around the left and right axis P1 is provided. Is allowed in the range of the elongated hole of the adjustment hole 91C. For example, when the engine 8 is driven and the forward / reverse switching lever 26 is operated forward, the cutting blade 10 connected to the lower end of the transmission case 7 is allowed in the adjustment hole 91C from the height H1 substantially horizontal to the ground. Tilt in range. And the rear-end part of the linkage rod 93 contacts the front-end | tip of the adjustment hole 91C, the height of the lower end part of the cutting blade 10 is automatically changed to the height H3, and the height H3 is maintained. .

  When the engine 8 is stopped or when the forward / reverse switching lever 26 is operated to the stop side (neutral side), the height of the cutting blade 10 is automatically changed to a height H1 substantially horizontal to the ground.

  By configuring the cutting height adjusting mechanism 90 as described above, the transmission case 7 can be changed by changing the linkage position of the rear end portion of the linkage rod 93 to the adjustment holes 91A, 91B, 91C by removing the pin 94. The height of the lower end portion of the cutting blade 10 can be changed and adjusted in three stages H1, H2, and H3, and the cutting height by the cutting blade 10 (before the cutting blade 10 to be described later) can be changed. The downward inclination angle α (rear downward inclination angle α)) can be changed and adjusted in three stages.

[Explanation of the cutting blade inclination]
Based on FIG.13 and FIG.14, the inclination condition of the cutting blade 10 is demonstrated. FIG. 13 shows the state of inclination of the cutting blade 10 in the forwardly lowered inclination posture where the traveling machine body 1 is moved forward, and FIG. 14 shows the state of inclination of the cutting blade 10 in the rearwardly lowered inclination posture where the traveling body 1 is moved backward. Show.

  As shown in FIG. 13, when the cutting blade 10 is substantially level with the non-rotating ground, when the engine 8 is driven and the forward / reverse switching lever 26 is switched to the forward side, the drive shaft 7 a is directed left and right. It rotates clockwise around the axis P1 as indicated by the black arrow in FIG. When the drive shaft 7a rotates clockwise, the force in the counterclockwise direction opposite to the direction of rotation of the drive shaft 7a indicated by the black arrow in FIG. 13 acts on the transmission case 7 according to the law of action and reaction of force. . When a counterclockwise force is applied to the transmission case 7, the transmission case 7, the engine 8 coupled to the transmission case 7, and the cutting blade 10 are integrally swung forward about the left and right axis P1, and the cutting height is increased. The swing range is regulated by the height adjusting mechanism 90 (in FIG. 13, when the cutting height is set to H3), the transmission case 7, the engine 8 and the cutting blade 10 are inclined downward by an angle α from the horizontal level. Become.

  On the other hand, as shown in FIG. 14, when the engine 8 is driven and the forward / reverse switching lever 26 is switched to the reverse side from a state where the cutting blade 10 is substantially horizontal with the non-rotating ground, the drive shaft 7a is moved to the left and right. It rotates counterclockwise as indicated by the black arrow in FIG. When the drive shaft 7a rotates counterclockwise, a force in the clockwise direction opposite to the direction in which the drive shaft 7a rotates indicated by the black arrow in FIG. . When a clockwise force is applied to the transmission case 7, the transmission case 7, and the engine 8 and the cutting blade 10 connected to the transmission case 7 are integrally swung backward about the left and right axis P1, and the cutting height is increased. The swinging range is regulated by the adjusting mechanism 90 (in FIG. 14, when the cutting height is set to H3), the transmission case 7, the engine 8 and the cutting blade 10 are inclined downward by an angle α from the horizontal level. Become.

  That is, when the engine 8 is driven to switch the forward / reverse switching lever 26 to the forward side or the reverse side and the traveling machine body 1 is moved forward or backward, the cutting blade is automatically set to the cutting height set by the cutting height adjusting mechanism 90. 10 swings automatically, and the cutting operation can be performed with the cutting height of the cutting blade 10 set in advance by the cutting height adjusting mechanism 90.

  As described above, the lower end portion (front end portion or rear end portion) of the cutting blade 10 which is inclined forwardly or backwardly downward by cutting the grass with the cutting blade 10 tilted forwardly or backwardly is most grass. The gap between the cutting blade 10 and the grass (ground) passing below the cutting blade 10 gradually becomes wider as the position becomes closer to the (ground) and moves in the opposite direction to the traveling direction from that position. Become. As a result, the contact area between the lower surface side of the cutting blade 10 and the grass (ground) passing through the lower side of the cutting blade 10 is reduced, and the resistance from the cut grass (ground) acting on the lower surface side of the cutting blade 10 is reduced. It becomes small and the load which acts on the cutting blade 10 at the time of cutting grass can be reduced.

  As a result, for example, the power for driving the cutting blade 10 to rotate (the power for cutting the grass) is reduced compared to a case where the cutting blade 10 is configured to cut grass in a state of being substantially horizontal with the ground, and the engine 8 is downsized. In addition, the weight reduction can be realized (for example, an engine with a small horsepower can be set while securing the ability to cut grass), and the walking-type grass mower can be made compact and lightweight.

[First Alternative Embodiment of the Invention]
In the above-mentioned [Best Mode for Carrying Out the Invention], the drive shaft 7a and the swing support shaft 7b extending from the transmission case 7 of the traveling machine body 1 are supported so as to be swingable around the left and right axis P1. Thus, the example in which the tilting posture changing mechanism is configured to change the posture of the cutting blade 10 to the forward downward tilting posture and the rearward downward tilting posture is shown. Different configurations may be adopted as long as they are supported in a movable manner.

  Specifically, for example, a configuration (not shown) that supports the cutting blade 10 so as to be swingable around the left and right axial centers may be employed in the lower portion of the transmission case 7. In addition to the engine 8 and the transmission case 7, A configuration (not shown) in which the cutting blade 10 is supported on the body frame 2 so as to be swingable around the left and right axis may be employed.

[Second Embodiment of the Invention]
In the above-mentioned [Best Mode for Carrying Out the Invention] and [First Alternative Embodiment], the power from the drive shaft 7a is transmitted to the front wheels 5 and the rear wheels 6 via the chain transmission mechanism 9. However, the power from the drive shaft 7a may be transmitted to the front wheels 5 and the rear wheels 6 through different transmission mechanisms. For example, a belt such as a V belt or a timing belt may be used. A transmission mechanism (not shown) may be adopted, and a drive shaft (not shown) may be adopted.

  In the above-mentioned [Best Mode for Carrying Out the Invention] and [First Different Embodiment of the Invention], the cutting rod height adjusting mechanism 90 is obtained by linking the linkage rod 93 across the bracket 91 and the bracket 92. However, a different mechanism may be employed as the cutting height adjusting mechanism 90, and for example, the upper limit of the swing range of the swinging engine 8 or the transmission case 7 is restricted to the body frame 2 side. The cutting height adjusting mechanism 90 may be configured to provide a restricting tool (not shown).

  In the above-mentioned [Best Mode for Carrying Out the Invention] and [First Alternative Embodiment], the cutting height adjusting mechanism 90 is adjusted so that the cutting height by the cutting blade 10 can be changed and adjusted in three stages. However, the cutting height of the cutting blade 10 can be changed and adjusted at different stages (for example, as few as two stages, or as many as four, five, etc.). The height adjustment mechanism 90 may be configured. In addition, the cutting height adjustment mechanism 90 may be configured so that the cutting height by the cutting blade 10 can be changed and adjusted steplessly, instead of changing the cutting height stepwise. Fine adjustment of the cutting height by the cutting blade 10 can be performed, and the workability of the cutting work can be further improved.

  Specifically, for example, a restricting tool (not shown) that restricts the upper limit of the swing range of the swinging engine 8 or the transmission case 7 is provided on the side of the body frame 2 that does not swing, and this restricting tool is adjusted. Accordingly, the cutting height adjusting mechanism 90 is configured so that the upper limit of the swing range of the engine 8 or the transmission case 7 is steplessly regulated.

[Third Another Embodiment of the Invention]
Instead of the cutting blade 10 in the above-mentioned [Best Mode for Carrying Out the Invention], [First Alternative Embodiment of the Invention] and [Second Alternative Embodiment of the Invention], a bar blade (not shown) May be adopted.

  In the above-mentioned [Best Mode for Carrying Out the Invention], [First Alternative Embodiment of the Invention] and [Second Alternative Embodiment of the Invention], the front wheels 5 and the rear wheels 6 are employed as the traveling devices. Although an example is shown, instead of the front wheel 5 and the rear wheel 6, a three-wheel traveling specification (not shown) in which three wheels are arranged, or a crawler traveling device (not shown) may be adopted.

  In the above-mentioned [Best Mode for Carrying Out the Invention], [First Alternative Embodiment] and [Second Alternative Embodiment], the front wheels 5 and the rear wheels 6 are driven by the power from the engine 8. However, the walking-type grass mower is configured so that the front wheels 5 or the rear wheels 6 are idle wheels, and the front wheels 5 or the rear wheels 6 are driven by the power from the engine 8. May be.

  In the above-mentioned [Best Mode for Carrying Out the Invention], [First Alternative Embodiment of the Invention] and [Second Alternative Embodiment of the Invention], a mower employing the engine 8 as the prime mover E is provided. As shown in the example, a different configuration may be adopted as the driving part E, for example, an electric motor (not shown) driven by electric power such as a battery or a commercial power source may be adopted instead of the engine 8.

  In the above-mentioned [Best Mode for Carrying Out the Invention], [First Alternative Embodiment of the Invention] and [Second Alternative Embodiment of the Invention], the engine 8 is connected to the upper portion of the transmission case 7 in an interlocking manner. However, a driving part E (not shown) in which the transmission case 7 and the engine 8 are integrally formed may be employed. Further, for simplicity, the transmission case 7 may be omitted, and the driving part E may be configured by only the engine 8 (not shown). In this case, the drive shaft and the swinging support shaft extending in the left-right direction from the engine 8 to the traveling device (wheels and the like) are extended, and the downward transmission shaft from the lower portion of the engine 8 to the cutting blade 10 is extended. The body frame 2 is supported so as to be swingable around the left and right axis (not shown).

1 traveling body 5 front wheel (traveling device)
6 Rear wheels (travel device)
7a Drive shaft 7b Oscillating support shaft 10 Cutting blade 90 Cutting height adjustment mechanism (tilt angle adjustment mechanism)
E Driving part P1 shaft center (left and right shaft center)
P2 axis (vertical axis)
α Forward descending tilt angle, backward descending tilt angle

  The present invention relates to a walking mower having a traveling machine body that includes a driving unit, a traveling device that rotates by power from the driving unit, and a cutting blade.

  As a conventional technique, for example, as disclosed in Patent Document 1, an engine (5 in FIG. 1 of Patent Document 1) is mounted on a traveling machine body having traveling wheels (4 in FIG. 1 of Patent Document 1). A walking type mower having a cutting blade (2 in FIG. 1 of Patent Document 1) that rotates by power from the engine is known.

Japanese Patent Laid-Open No. 2007-53991 (see FIGS. 1, 2, 13, and 14)

  In the walking type mower of Patent Document 1, the base (66 in FIG. 13 of Patent Document 1) and the blade piece (67 in FIG. 13 of Patent Document 1) constituting the cutting blade are driven so as to be substantially horizontal with the ground. When a cutting blade is attached to the lower part of the case (9 in FIG. 13 of Patent Document 1) and the walking type grass mower is advanced, the grass introduced from the front is cut off at the front part of the cutting blade, and the walking type grass cutting machine. When the machine is moved backward, the grass introduced from behind is cut off at the rear part of the cutting blade.

Therefore, although the part of the cutting blade that actually cuts the grass is the front part or the rear part of the cutting blade, even when the walking type grass mower is advanced, even when the walking type grass mower is moved backward, The lower surface side of the cutting blade was located at a position close to the ground over almost the entire area, and the grass growing on the ground after being cut through the lower side of the cutting blade was likely to become a resistance to rotate the cutting blade. . As a result, the load on the engine due to the driving of the cutting blade is increased, and there is room for improvement from the viewpoint of reducing the size of the engine and reducing the weight of the walking type mower.
The present invention has a simple structure for a walk-type grass mower capable of saving the power to rotate the cutting blade while enabling the cutting operation by moving the traveling body forward and the cutting operation by moving the traveling body backward. It aims to be realized with.

The walking type mower of the present invention is a walking type mower having a driving unit, a driving unit, a traveling device that rotates by power from the driving unit, and a cutting blade. In a state where the cutting blade is supported rotatably about the vertical axis, the driving unit and the cutting blade are swingably supported around the left and right axial centers, and the traveling device is in contact with the ground plane. The cutting blade is not grounded to the grounding surface, and the driving portion and the cutting blade are supported by the traveling machine body, and the forward cutting inclination posture in which the front side of the cutting blade swings downward, and the cutting blade An inclination posture changing mechanism is provided for changing the posture of the driving unit and the cutting blade in a downward inclination posture after the rear side swings downward.

In the above configuration, it is preferable that the traveling device includes left and right front wheels and left and right rear wheels supported by the traveling machine body.

The said structure WHEREIN: It is suitable when the steering handle is provided in the said traveling body.

Overall left side view of walking mower Overall plan view of walking type mower Longitudinal left side view of traveling aircraft Cross-sectional plan view of traveling aircraft Longitudinal rear view of traveling aircraft A longitudinal rear view for explaining the support structure of the front and rear wheels Vertical side view explaining the structure of the movable shatterproof cover Cross-sectional plan view explaining the structure of the cutting blade Transmission system diagram of walking type mower Longitudinal rear view showing the power transmission structure of a walking mower Cross-sectional plan view showing the transmission structure of a walking type mower Perspective view of cutting blade clutch Schematic right side view explaining the state of inclination of the cutting blade when it is moved forward Schematic right side view explaining the state of inclination of the cutting blade when it is moved backward

[Walking mower overall configuration]
Based on FIGS. 1-6, the whole structure of a walk-type mower is demonstrated. 1 and 2 show an overall left side view and an overall plan view of the walking mower, respectively, and FIGS. 3 to 5 show a longitudinal left side view, a transverse plan view, and a longitudinal rear view of the traveling machine body 1, respectively. . FIG. 6 is a longitudinal rear view for explaining the support structure of the front wheel 5 and the rear wheel 6.

  As shown in FIGS. 1 and 2, a front axle 3 and a rear axle 4 are pivotally supported on a body frame 2 mounted on the traveling body 1, and left and right end portions of the front axle 3 and the rear axle 4 are supported. The front wheels 5 and 5 and the rear wheels 6 and 6 (corresponding to traveling devices) made of sheet metal are fixed to each. A transmission case 7 is supported on the upper part of the machine body frame 2 so as to be swingable around a left and right axis P1, and an engine 8 integrally formed with a fuel tank 8a is interlocked and connected to the upper part of the transmission case 7. Thus, the driving part E is configured. The engine 8 is equipped with a recoil type starter 8b, and the engine 8 can be driven by the starter 8b.

  A chain transmission mechanism 9 is disposed on the right side of the traveling machine body 1, and the power from the engine 8 is transmitted to the chain transmission mechanism 9 via a transmission path in the transmission case 7 so that the front axle 3 and the rear axle are transmitted. 4 rotates, and the left and right front wheels 5 and rear wheels 6 rotate. A cutting blade 10 is attached to the lower part of the transmission case 7, and the power from the engine 8 is transmitted to the cutting blade 10 via a transmission path in the transmission case 7, so that the cutting blade 10 rotates and cuts grass. It is configured to be able to.

  As shown in FIGS. 4 and 5, a U-shaped frame 18 is fixed to the upper part of the body frame 2 in a plan view, and an end of the frame 18 extending leftward from the body frame 2. The support shaft 19 is supported by the portion so as to be rotatable around a vertical axis. A bracket 20 is supported on the upper end portion of the support shaft 19 so as to be rotatable around a lateral axis, and a pipe-like steering handle 21 is fixed to the bracket 20.

  As shown in FIG. 1 and FIG. 2, the steering handle 21 is swingable about the vertical axis and is set in advance by the action of the first lock mechanism 22 provided between the steering handle 21 and the frame 18. It is configured so that it can be selectively fixed and held at a plurality of swing positions around the vertical axis, and is swingable about the horizontal axis, and is provided between the frame 18 and a second frame. By the action of the lock mechanism 23, the lock mechanism 23 can be selectively fixed and held at a plurality of swing positions around a preset lateral axis.

  The extending end of the steering handle 21 is equipped with a grip 21a. The first release that enables the grip 21a to be unlocked by the first lock mechanism 22 that is spring-biased in a locked state. The lever 24 and the second release lever 25 that enables the unlocking operation of the second lock mechanism 23 spring-biased in the locked state are attached, and are linked to the first and second lock mechanisms 22 and 23, respectively. Yes.

  A main clutch lever 21b is mounted on the extending end of the steering handle 21 so as to be swingable up and down around a lateral axis, and is linked to a main clutch 63, which will be described later, to rotate the cutting blade 10. It is comprised so that a stop and the traveling body 1 can be stopped.

  A forward / reverse switching lever 26 that can be switched to a forward position, a neutral position, and a backward position is supported at the rear end of the steering handle 21 so as to be swingable to the left and right around a vertical axis. An operation arm 85, which will be described later, is linked to the lever 26 so that the walking type mower can be switched forward, stop (neutral), and reverse by operating the forward / reverse switching lever 26.

  As shown in FIGS. 3, 4, and 6, the fuselage frame 2 is provided across right and left main frames 31, 32 that are long in the front-rear direction and front ends of the right and left main frames 31, 32. A front frame 33 and a rear frame 34 provided over rear ends of the right and left main frames 31 and 32 are provided.

  The front and rear frames 33 and 34 are constituted by cylindrical members, and the front axle 3 facing left and right is rotatably fitted to the front frame 33 via left and right bearing members 37. A left and right rear axle 4 is rotatably fitted in the rear frame 34 via left and right bearing members 38.

  A front rod 35 that protects the front part of the traveling machine body 1 is mounted over the front ends of the right and left main frames 31 and 32, and the traveling machine body 1 is installed over the rear ends of the right and left main frames 31 and 32. A rear rod 36 for protecting the rear portion is mounted.

  As shown in FIGS. 3 to 5, a drive shaft 7 a extends rightward from the transmission case 7, and this drive shaft 7 a is rotatably supported by a right main frame 31 via a bearing member 39. ing. A swing support shaft 7b concentric with the drive shaft 7a extends from the transmission case 7 to the left. The swing support shaft 7b extends to the left main frame 32 via a bearing member 40 and has a left-right axis. It is rotatably supported around P1. As a result, the transmission case 7, the engine 8 attached to the transmission case 7, the cutting blade 10 and the like can be supported integrally with the body frame 2 so as to be able to swing back and forth around the axis P1 in the left-right direction.

  The positions of the driving shaft 7a and the swinging support shaft 7b in the front-rear direction in the lateral direction of the axial center P1 are the transmission case 7, the engine 8 and the cutting blade 10 supported by the drive shaft 7a and the swinging support shaft 7b. When the driving shaft 7a is stopped and no inertial force is applied to the transmission case 7 or the like, the cutting blade 10 is substantially horizontal with the ground. In a state where the drive shaft 7a is rotated and the inertial force acts on the transmission case 7 and the like, the inertial force generated by rotating the drive shaft 7a by the force around the axis P1 due to the weight of the transmission case 7 and the like is maintained. This is configured so that the cutting blade 10 is changed in posture to a front-falling inclination posture and a rear-falling inclination posture (see FIGS. 13 and 14).

  As shown in FIGS. 3 to 6, a chain transmission mechanism 9 is provided on the right outer side of the right main frame 31. The chain transmission mechanism 9 includes a drive sprocket 41 linked to the right outer end of the drive shaft 7a, a front sprocket 42 linked to the right outer end of the front axle 3, and a right outer portion of the rear axle 4. The rear sprocket 43 linked to the end, the tension sprocket 44 disposed on the top of the drive sprocket 41, the drive sprocket 41, the front and rear sprockets 42 and 43, and the tension sprocket 44 And a transmission chain 45 provided.

  A right side surface of the right main frame 31 is provided with a chain cover 46 that is divided into left and right parts. The left chain cover 46a is fixed to the right main frame 31, and the left chain cover 46a is attached to the right outer side. The chain transmission mechanism 9 can be covered with the chain cover 46 by tightening and fixing the right chain cover 46b from the side.

  A tension sprocket 44 is supported at the upper part of the front and rear central part of the left chain cover 46a so as to be rotatable about a left and right axis. The tension sprocket 44 is attached to the left chain cover 46a so that its position can be changed in the vertical direction. The tension sprocket 44 is configured so that the tension of the transmission chain 45 can be adjusted by adjusting the position of the tension sprocket 44 in the vertical direction. .

  A cover 50 is detachably attached to the front and rear center portion of the right chain cover 46b from the right outer side, and the inside of the chain cover 46 can be inspected by removing the cover 50.

  Left and right front wheels 5 and 5 and rear wheels 6 and 6 are externally fitted and inserted into the left and right ends of the front axle 3 and the rear axle 4 from the laterally outer side, so that the front axle 3 and the rear axle 4 rotate together. It is fixed so that it can move. When the power from the engine 8 is transmitted to the drive shaft 7a through the transmission case 7 and the front axle 3 and the rear axle 4 rotate through the chain transmission mechanism 9, the front wheels 5 and the rear wheels 6 rotate, and walking type mowing. The machine is configured to move forward or backward.

  As described above, the drive shaft 7a and the swing support shaft 7b extending from the transmission case 7 are supported on the body frame 2 of the traveling machine body 1 so as to be swingable around the axis P1 in the left-right direction. When the traveling machine body 1 is advanced by transmitting power to the drive shaft 7a through the transmission case 7, and rotating the front wheels 5 and the rear wheels 6 through the chain transmission mechanism 9 by the power from the drive shaft 7a, the cutting blade An inclination posture changing mechanism in which the posture is changed to a forward downward inclined posture in which the front side of 10 is swung downward, and the posture is changed to a downward inclined posture after the rear side of the cutting blade 10 is swung downward when the traveling machine body 1 is moved backward. (See FIGS. 13 and 14).

[Detailed structure of the cover]
Based on FIGS. 4-7, the detailed structure of the cover with which the traveling body 1 is mounted | worn is demonstrated. FIG. 7 shows a longitudinal side view of the structure of the movable scattering prevention cover 54 as viewed from the inside of the machine body.

  As shown in FIGS. 4 and 5, left and right upper covers 51 are fixed to the lower surfaces of the front and rear central portions of the right and left main frames 31, 32, and left and right upper covers 51 are prevented from fixing left and right fixed scattering. The cover 52 is fixed. The gap between the lower end of the left fixed anti-scatter cover 52 and the ground is set wider than the gap between the lower end of the right anti-scatter cover 52 and the ground, and the left anti-scatter cover 52 will be described later. In cooperation with the movable scattering prevention cover 54, it is configured to prevent scattering of the cut grass to the left side.

  As shown in FIGS. 5 and 7, front and rear brackets 53 extend downward from the frame 18, and a movable scattering prevention cover 54 is attached to the front and rear brackets 53. The movable scattering prevention cover 54 has long front and rear long holes 54A formed in the vertical direction, and front and rear pins 53A extending leftward from the front and rear brackets 53 are communicated with the front and rear long holes 54A. . A spring mounting portion 54 a that protrudes inward is provided on the upper part of the movable scattering prevention cover 54, and an elastic spring 55 is mounted across the spring mounting portion 54 a and the front and rear brackets 53.

  The lower part of the front end portion of the movable scattering prevention cover 54 is formed with a front inclined portion 54b that is notched upward in the side view, and the rear lower portion of the movable scattering prevention cover 54 is rearward in the side view. A rear inclined portion 54c cut out upward is formed. As a result, for example, when an ambulatory mower is moved forward and an obstacle such as a stone from the front left side comes into contact with the movable scattering prevention cover 54, the biasing force of the elastic spring 55 is caused by the elongated hole 54A formed in the movable scattering prevention cover 54. The movable scattering prevention cover 54 moves upward against this. On the contrary, when the walking type mower is moved backward and an obstacle such as a stone comes into contact with the movable scattering prevention cover 54 from the left rear side, the urging force of the elastic spring 55 is resisted by the elongated hole 54A formed in the movable scattering prevention cover 54. Then, the movable scattering prevention cover 54 moves upward.

  As shown in FIGS. 4 and 5, the front part and the rear part of the movable scattering prevention cover 54 are arranged along the outer surfaces of the left front wheel 5 and the rear wheel 6, and the front end part and the rear end part are inward, respectively. The front end portion and the rear end portion bent inward are formed so as to overlap the front wheel 5 and the rear wheel 6 in plan view. Further, the gap between the lower end of the movable scattering prevention cover 54 and the ground is set to be substantially the same as the gap between the lower end of the right fixed scattering prevention cover 52 and the ground. Thereby, the clearance between the lower end of the movable scattering prevention cover 54 and the ground, and the clearance between the movable scattering prevention cover 54 and the front wheel 5 and the rear wheel 6 can be set small, and scattering of the cut grass to the left side can be effectively performed. Can be prevented.

  By configuring the movable scattering prevention cover 54 as described above, normally, the movable scattering prevention cover 54 is urged downward by the urging force of the elastic spring 55 to widely move between the front wheel 5 and the rear wheel 6. The anti-scattering cover 54 can be covered from the side, and when it comes into contact with an obstacle, the movable anti-scattering cover 54 moves upward against the urging force of the elastic spring 55 to damage the movable anti-scattering cover 54. Can be prevented. The movable scattering prevention cover 54 may be provided on the right side of the traveling machine body 1, and the movable scattering prevention cover 54 may be provided on both the left and right sides of the traveling machine body 1.

  As shown in FIGS. 3 and 6, the front frame 33 provided across the right and left main frames 31, 32 has a rubber front scattering prevention member 56 that covers the space between the left and right front wheels 5. A rear frame 34 that is swingably mounted back and forth around the axis in the left-right direction and that is provided over the right and left main frames 31, 32 is made of rubber that covers the space between the left and right rear wheels 6. The rear scattering prevention member 57 is mounted so as to be swingable back and forth around the axis in the left-right direction. The left and right end portions of the front and rear scattering prevention covers 56 and 57 are shaped so as to enter the inside of the front wheel 5 and the rear wheel 6, respectively, thereby effectively scattering the cutting grass forward and backward. Can be prevented.

  As shown in FIGS. 4 and 6, the body frame 2 is covered from above by front and rear upper covers 58 that are divided into front and rear parts. The center part of the front and rear upper covers 58 is formed in a shape bulging upward, the outer peripheral part is formed in a horizontal shape, and the left and right side parts formed in the horizontal shape of the front and rear upper cover 58 are right and right. It is fastened and fixed at a plurality of locations on the upper surface side of the left main frames 31 and 32.

[Detailed structure of the cutting blade]
Based on FIG.5 and FIG.8, the detailed structure of the cutting blade 10 is demonstrated. FIG. 8 is a cross-sectional plan view illustrating the structure of the cutting blade 10.

  As shown in FIGS. 5 and 8, the cutting blade 10 includes a boss member 11 that attaches the cutting blade 10 to the lower portion of the transmission case 7, a rotating disk 12 fixed to the boss member 11, and a rotating disk 12. And a plurality of cutting blade bodies 13 rotatably supported on the outer peripheral portion, and a plurality of diffusion blades 14 fixed to the upper surface side of the rotating disk 12.

  The rotating disk 12 is formed in a downward dish shape that is inclined outward and downward so that the distance from the ground gradually decreases outward from the fixing portion with the boss member 11, and the ground and A substantially horizontal horizontal portion 12a is formed. The cutting blade body 13 is composed of an upper cutting blade body 13a formed into a shape inclined obliquely outward and upward, and a lower cutting blade body 13b formed into a shape inclined obliquely outward and downward. The upper cutting blade body 13a and the lower cutting blade body 13b are alternately supported by the pins 15 at an equal pitch of about 90 degrees at a plurality of positions on the horizontal portion 12a on the outer peripheral portion of the rotating disk 12. Has been.

  The diffusion blades 14 are shaped so that the upper end portion thereof is inclined obliquely upward and upward so that the area of the blades gradually increases toward the outer side, and the cutting blade bodies adjacent to each other from the axis P2 Thirteen intermediate positions are arranged radially at an equal pitch of about 90 degrees.

  A cutting blade cover 16 is attached to the lower part of the transmission case 7, and the cutting blade cover 16 prevents the cutting grass from entering the rotation center side so that the cutting grass can be prevented from being wound around the rotation center. It is configured.

[Transmission structure of walking type mower]
Based on FIGS. 9-12, the transmission structure of a walk-type mower is demonstrated. FIG. 9 shows a transmission system diagram of the walking mower, and FIGS. 10 and 11 show a longitudinal rear view and a transverse plan view of the transmission structure of the walking mower, respectively. FIG. 12 is a perspective view of the cutting blade clutch 68.

  As shown in FIGS. 9 to 11, a vertical input shaft 62 is rotatably supported on the upper portion of the transmission case 7 via a pair of bearings 61, and the upper end portion of the input shaft 62 is connected to the transmission case 7. The main shaft 63 is connected to an output shaft 8c of the engine 8 fixed to the upper portion. A transmission gear 64 is connected to a lower portion of the input shaft 62 so as to be integrally rotatable. The transmission gear 64 is engaged with a transmission gear 72 that is interlocked and connected to an upper transmission shaft 65 described later.

  An upper transmission shaft 65 and a lower transmission shaft 66 that are concentrically disposed around a vertical axis P2 of the transmission case 7 are rotatably supported via a plurality of bearings 67. A cutting blade clutch 68 is mounted across the lower transmission shaft 66. The boss member 11 of the cutting blade 10 is fastened and fixed to the lower end portion of the lower transmission shaft 66 from below, and when the cutting blade clutch 68 is operated to the ingress side, the power from the engine 8 is input to the input shaft 62 and the upper transmission. The cutting blade 10 is configured to rotate by being transmitted to the lower transmission shaft 66 via the shaft 65 and the cutting blade clutch 68.

  As shown in FIGS. 10 and 12, the cutting blade clutch 68 can rotate integrally with the upper clutch 69 linked to the upper transmission shaft 65 and the lower transmission shaft 66 and can slide up and down by a spline structure. The upper clutch 69 and the lower clutch 70 are formed with engaging pieces 69a and 70a that are engaged with each other.

  An elastic spring 68a that urges the lower clutch 70 upward is mounted across the lower surface side of the lower clutch 70 and the upper surface side of the bearing 67, and the cutting blade clutch 68 is urged toward the entry side by the elastic spring 68a. It is comprised so that.

  The engaging pieces 69a and 70a are formed with inclined portions 69b and 70b that are inclined obliquely. When power from the engine 8 is transmitted to the lower transmission shaft 66 via the upper transmission shaft 65, the upper clutch The engagement piece 69 a of 69 and the engagement piece 70 a of the lower clutch 70 mesh with each other, and the power from the engine 8 is transmitted to the lower transmission shaft 66.

  For example, when the engine 8 is stopped and the rotation of the upper transmission shaft 65 is stopped, the cutting blade 10 is rotated by the inertial force, and the inertial force from the cutting blade 10 is transmitted from the lower transmission shaft 66 to the upper transmission shaft 65. As a result, the lower clutch 70 is rotated relative to the upper clutch 69 by the inclined portions 69b and 70b of the engagement pieces 69a and 70a, and the inertial force from the lower transmission shaft 66 is transmitted to the upper transmission shaft 65. Is cut off. When the rotation of the cutting blade 10 due to the inertial force stops, the lower clutch 70 is operated upward by the biasing force of the elastic spring 68a, and the cutting blade clutch 68 is operated on the entry side.

  As a result, it is possible to prevent the inertial force of the cutting blade 10 from rotating along the transmission upstream side (the engine 8 side and the drive shaft 7b side) (for example, the front wheel 5 and the rear wheel 6 are moved by the inertial force of the cutting blade 10). In addition, for example, a brake device (not shown) that forcibly brakes the rotation of the cutting blade 10 is provided on the transmission upstream side of the cutting blade 10 (for example, the upper transmission shaft 65 or the lower transmission shaft 66), and the engine 8 Compared to a configuration in which the inertial force due to the rotation of the cutting blade 10 when it is stopped is not transmitted to the transmission upstream side, the mechanism for suppressing the transmission of the inertial force from the cutting blade 10 to the transmission upstream side is simplified. Manufacturing costs can be reduced.

  The lower clutch 70 is formed with a shift groove 70c in the outer periphery of the lower portion of the lower clutch 70 so as to function as a shift member of the cutting blade clutch 68. When the operating portion 71a of the shift lever 71 supported so as to be swingable to the left and right is engaged and the lever main body 71b of the shift lever 71 is operated to swing, the lower clutch 70 slides up and down and the cutting blade clutch 68 is disconnected. It is configured to be able to contact.

  As shown in FIGS. 9 to 11, transmission gears 72 and 73 are interlocked to the upper transmission shaft 65, and the transmission gear 72 is engaged with a transmission gear 64 fixed to the input shaft 62. A transmission gear 75 is interlocked and connected to a transmission shaft 74 that is supported by the transmission case 7 in a freely rotating manner, and this transmission gear 75 is engaged with a transmission gear 73 that is interlocked and connected to the upper transmission shaft 65. The power from the upper transmission shaft 65 facing up and down is changed by 90 degrees and transmitted to the transmission shaft 74 facing front and rear. A transmission gear 76 is interlocked and connected to the transmission shaft 74, and this transmission gear 76 is engaged with a transmission gear 78 disposed on the lower right side of the transmission shaft 74 and interlocked and connected to the transmission shaft 77.

  A bevel gear 79 is interlocked to the transmission shaft 77, and the bevel gear 79 is engaged with a forward-bevel gear 80 and a backward-bevel gear 81 that are externally fitted to the left-right drive shaft 7a. The drive shaft 7a is supported by the transmission case 7 via a bearing 83 so as to be rotatable about a left and right axis P1, and forward and reverse bevel gears 80 and 81 are rotatable on the drive shaft 7a. The shift member 82 is externally fitted between the forward-bevel gear 80 and the backward-bevel gear 81 so as to be slidable in the left-right direction and to be rotatable integrally with the drive shaft 7a.

  In the transmission case 7, an operation shaft 84 is supported so as to be rotatable around a vertical axis, and an operation arm 85 and upper and lower operation members 86 are connected to an upper end portion and a lower end portion of the operation shaft 84. Yes. A shift groove 82a is formed on the outer periphery of the shift member 82, and an operation member 86 connected to the operation shaft 84 is engaged with the shift groove 82a. When the operation arm 85 is swung back and forth, the shift member 82 slides in the left-right direction and meshes with the forward-bevel gear 80 or the backward-bevel gear 81 so that the traveling machine body 1 can be switched between forward, stop (neutral), and reverse. It is configured. Thus, the forward / reverse clutch 87 is constituted by the bevel gear 79, the forward bevel gear 80, the reverse bevel gear, the shift member 82, and the like.

  As shown in FIGS. 1 and 2, the operating arm 85 is linked to the forward / reverse switching lever 26 provided on the steering handle 21, and when the forward / backward switching lever 26 is operated to swing forward (left side), The operating arm 85 is swung backward, the shift member 82 is engaged with the forward bevel gear 80, the forward / reverse clutch 87 is operated to enter the forward side, and the power from the bevel gear 79 is transmitted via the forward bevel gear 80 and the shift member 82. Is transmitted to the drive shaft 7a, and the drive shaft 7a is driven to rotate forward. On the other hand, when the forward / reverse switching lever 21 is swung to the reverse side (right side), the operation arm 85 is swung forward, the shift member 82 is engaged with the reverse bevel gear 81, and the forward / reverse clutch 87 enters the reverse side. By being operated, the power from the bevel gear 79 is transmitted to the drive shaft 7a via the reverse bevel gear 81 and the shift member 82, and the drive shaft 7a is driven to rotate in reverse.

  As shown in FIGS. 9 to 11, the drive sprocket 41 of the chain transmission mechanism 9 is interlocked with the right end portion of the drive shaft 7 a, and the power from the drive shaft 7 a is forwarded via the chain transmission mechanism 9. The transmission is transmitted to the axle 3 and the rear axle 4 so that the front wheels 5 and the rear wheels 6 are rotated forward and backward, and the traveling machine body 1 moves forward or backward.

[Detailed structure of cutting height adjustment mechanism]
Based on FIG.3 and FIG.4, the detailed structure of the cutting height adjustment mechanism 90 (equivalent to an inclination angle adjustment mechanism) is demonstrated. As shown in FIGS. 3 and 4, the connecting rod spans between a bracket 91 clamped and fixed to the upper surface of the rear portion of the left main frame 32 and a plate-shaped bracket 92 clamped and fixed to the left side of the transmission case 7. The cutting height adjusting mechanism 90 that regulates the lower limit range of the cutting height is configured by linking 93.

  The bracket 91 is formed by bending a plate material into an L shape, and three adjustment holes 91A, 91B, 91C are processed in a portion extending upward from a portion fixed to the left main frame 32. Yes. The upper adjustment hole 91A is formed into a round hole, and the center adjustment hole 91B and the lower adjustment hole 91C are each formed into a long long hole in the front and rear direction. The lengths of the elongated holes of the adjustment holes 91B and 91C are set so as to gradually increase so that the cutting heights H1, H2, and H3, which will be described later, increase at substantially equal intervals.

  The front end portion and the rear end portion of the linkage rod 93 are formed to be bent inward and outward, respectively, and the front end portion of the linkage rod 93 is linked to the left and right through holes in the upper portion of the bracket 92. By connecting the rear end portion of the linkage rod 93 to any one of the adjustment holes 91A, 91B, 91C of the bracket 91 with the pin 94, the swing range of the transmission case 7 and the like around the left-right axis P1 It is comprised so that the upper limit of can be regulated.

  Even if the rear end portion of the linkage rod 93 is linked to the adjustment hole 91A, the swinging of the transmission case 7 around the left and right axis P1 is restricted, and the cutting blade 10 is rotated by driving the engine 8. The height of the lower end portion of the cutting blade 10 remains H1 and does not change.

  When the rear end portion of the linkage rod 93 is linked to the adjustment hole 91B, the movement of the rear end portion of the linkage rod 93 is allowed in the range of the elongated hole of the adjustment hole 91B, and the transmission case 7 around the axis P1 in the left-right direction. Is allowed in the range of the elongated hole of the adjustment hole 91B. For example, when the engine 8 is driven and the forward / reverse switching lever 26 is operated forward, the cutting blade 10 connected to the lower end of the transmission case 7 is allowed in the adjustment hole 91B from the height H1 substantially horizontal to the ground. Tilt in range. And the rear-end part of the linkage rod 93 contacts the front-end | tip of the adjustment hole 91B, the height of the lower end part of the cutting blade 10 is automatically changed into height H2, and the height H2 is maintained. .

  When the rear end portion of the linkage rod 93 is linked to the adjustment hole 91C, the movement of the rear end portion of the linkage rod 93 is allowed in the range of the long hole of the adjustment hole 91C, and the transmission case 7 around the left and right axis P1 is provided. Is allowed in the range of the elongated hole of the adjustment hole 91C. For example, when the engine 8 is driven and the forward / reverse switching lever 26 is operated forward, the cutting blade 10 connected to the lower end of the transmission case 7 is allowed in the adjustment hole 91C from the height H1 substantially horizontal to the ground. Tilt in range. And the rear-end part of the linkage rod 93 contacts the front-end | tip of the adjustment hole 91C, the height of the lower end part of the cutting blade 10 is automatically changed to the height H3, and the height H3 is maintained. .

  When the engine 8 is stopped or when the forward / reverse switching lever 26 is operated to the stop side (neutral side), the height of the cutting blade 10 is automatically changed to a height H1 substantially horizontal to the ground.

  By configuring the cutting height adjusting mechanism 90 as described above, the transmission case 7 can be changed by changing the linkage position of the rear end portion of the linkage rod 93 to the adjustment holes 91A, 91B, 91C by removing the pin 94. The height of the lower end portion of the cutting blade 10 can be changed and adjusted in three stages H1, H2, and H3, and the cutting height by the cutting blade 10 (before the cutting blade 10 to be described later) can be changed. The downward inclination angle α (rear downward inclination angle α)) can be changed and adjusted in three stages.

[Explanation of the cutting blade inclination]
Based on FIG.13 and FIG.14, the inclination condition of the cutting blade 10 is demonstrated. FIG. 13 shows the state of inclination of the cutting blade 10 in the forwardly lowered inclination posture where the traveling machine body 1 is moved forward, and FIG. 14 shows the state of inclination of the cutting blade 10 in the rearwardly lowered inclination posture where the traveling body 1 is moved backward. Show.

  As shown in FIG. 13, when the cutting blade 10 is substantially level with the non-rotating ground, when the engine 8 is driven and the forward / reverse switching lever 26 is switched to the forward side, the drive shaft 7 a is directed left and right. It rotates clockwise around the axis P1 as indicated by the black arrow in FIG. When the drive shaft 7a rotates clockwise, the force in the counterclockwise direction opposite to the direction of rotation of the drive shaft 7a indicated by the black arrow in FIG. 13 acts on the transmission case 7 according to the law of action and reaction of force. . When a counterclockwise force is applied to the transmission case 7, the transmission case 7, the engine 8 coupled to the transmission case 7, and the cutting blade 10 are integrally swung forward about the left and right axis P1, and the cutting height is increased. The swing range is regulated by the height adjusting mechanism 90 (in FIG. 13, when the cutting height is set to H3), the transmission case 7, the engine 8 and the cutting blade 10 are inclined downward by an angle α from the horizontal level. Become.

  On the other hand, as shown in FIG. 14, when the engine 8 is driven and the forward / reverse switching lever 26 is switched to the reverse side from a state where the cutting blade 10 is substantially horizontal with the non-rotating ground, the drive shaft 7a is moved to the left and right. It rotates counterclockwise as indicated by the black arrow in FIG. When the drive shaft 7a rotates counterclockwise, a force in the clockwise direction opposite to the direction in which the drive shaft 7a rotates indicated by the black arrow in FIG. . When a clockwise force is applied to the transmission case 7, the transmission case 7, and the engine 8 and the cutting blade 10 connected to the transmission case 7 are integrally swung backward about the left and right axis P1, and the cutting height is increased. The swinging range is regulated by the adjusting mechanism 90 (in FIG. 14, when the cutting height is set to H3), the transmission case 7, the engine 8 and the cutting blade 10 are inclined downward by an angle α from the horizontal level. Become.

  That is, when the engine 8 is driven to switch the forward / reverse switching lever 26 to the forward side or the reverse side and the traveling machine body 1 is moved forward or backward, the cutting blade is automatically set to the cutting height set by the cutting height adjusting mechanism 90. 10 swings automatically, and the cutting operation can be performed with the cutting height of the cutting blade 10 set in advance by the cutting height adjusting mechanism 90.

  As described above, the lower end portion (front end portion or rear end portion) of the cutting blade 10 which is inclined forwardly or backwardly downward by cutting the grass with the cutting blade 10 tilted forwardly or backwardly is most grass. The gap between the cutting blade 10 and the grass (ground) passing below the cutting blade 10 gradually becomes wider as the position becomes closer to the (ground) and moves in the opposite direction to the traveling direction from that position. Become. As a result, the contact area between the lower surface side of the cutting blade 10 and the grass (ground) passing through the lower side of the cutting blade 10 is reduced, and the resistance from the cut grass (ground) acting on the lower surface side of the cutting blade 10 is reduced. It becomes small and the load which acts on the cutting blade 10 at the time of cutting grass can be reduced.

  As a result, for example, the power for driving the cutting blade 10 to rotate (the power for cutting the grass) is reduced compared to a case where the cutting blade 10 is configured to cut grass in a state of being substantially horizontal with the ground, and the engine 8 is downsized. In addition, the weight reduction can be realized (for example, an engine with a small horsepower can be set while securing the ability to cut grass), and the walking-type grass mower can be made compact and lightweight.

[First Alternative Embodiment of the Invention]
In the above-mentioned [Best Mode for Carrying Out the Invention], the drive shaft 7a and the swing support shaft 7b extending from the transmission case 7 of the traveling machine body 1 are supported so as to be swingable around the left and right axis P1. Thus, the example in which the tilting posture changing mechanism is configured to change the posture of the cutting blade 10 to the forward downward tilting posture and the rearward downward tilting posture is shown. Different configurations may be adopted as long as they are supported in a movable manner.

  Specifically, for example, a configuration (not shown) that supports the cutting blade 10 so as to be swingable around the left and right axial centers may be employed in the lower portion of the transmission case 7. In addition to the engine 8 and the transmission case 7, A configuration (not shown) in which the cutting blade 10 is supported on the body frame 2 so as to be swingable around the left and right axis may be employed.

[Second Embodiment of the Invention]
In the above-mentioned [Best Mode for Carrying Out the Invention] and [First Alternative Embodiment], the power from the drive shaft 7a is transmitted to the front wheels 5 and the rear wheels 6 via the chain transmission mechanism 9. However, the power from the drive shaft 7a may be transmitted to the front wheels 5 and the rear wheels 6 through different transmission mechanisms. For example, a belt such as a V belt or a timing belt may be used. A transmission mechanism (not shown) may be adopted, and a drive shaft (not shown) may be adopted.

  In the above-mentioned [Best Mode for Carrying Out the Invention] and [First Different Embodiment of the Invention], the cutting rod height adjusting mechanism 90 is obtained by linking the linkage rod 93 across the bracket 91 and the bracket 92. However, a different mechanism may be employed as the cutting height adjusting mechanism 90, and for example, the upper limit of the swing range of the swinging engine 8 or the transmission case 7 is restricted to the body frame 2 side. The cutting height adjusting mechanism 90 may be configured to provide a restricting tool (not shown).

  In the above-mentioned [Best Mode for Carrying Out the Invention] and [First Alternative Embodiment], the cutting height adjusting mechanism 90 is adjusted so that the cutting height by the cutting blade 10 can be changed and adjusted in three stages. However, the cutting height of the cutting blade 10 can be changed and adjusted at different stages (for example, as few as two stages, or as many as four, five, etc.). The height adjustment mechanism 90 may be configured. In addition, the cutting height adjustment mechanism 90 may be configured so that the cutting height by the cutting blade 10 can be changed and adjusted steplessly, instead of changing the cutting height stepwise. Fine adjustment of the cutting height by the cutting blade 10 can be performed, and the workability of the cutting work can be further improved.

  Specifically, for example, a restricting tool (not shown) that restricts the upper limit of the swing range of the swinging engine 8 or the transmission case 7 is provided on the side of the body frame 2 that does not swing, and this restricting tool is adjusted. Accordingly, the cutting height adjusting mechanism 90 is configured so that the upper limit of the swing range of the engine 8 or the transmission case 7 is steplessly regulated.

[Third Another Embodiment of the Invention]
Instead of the cutting blade 10 in the above-mentioned [Best Mode for Carrying Out the Invention], [First Alternative Embodiment of the Invention] and [Second Alternative Embodiment of the Invention], a bar blade (not shown) May be adopted.

  In the above-mentioned [Best Mode for Carrying Out the Invention], [First Alternative Embodiment of the Invention] and [Second Alternative Embodiment of the Invention], the front wheels 5 and the rear wheels 6 are employed as the traveling devices. Although an example is shown, instead of the front wheel 5 and the rear wheel 6, a three-wheel traveling specification (not shown) in which three wheels are arranged, or a crawler traveling device (not shown) may be adopted.

  In the above-mentioned [Best Mode for Carrying Out the Invention], [First Alternative Embodiment] and [Second Alternative Embodiment], the front wheels 5 and the rear wheels 6 are driven by the power from the engine 8. However, the walking-type grass mower is configured so that the front wheels 5 or the rear wheels 6 are idle wheels, and the front wheels 5 or the rear wheels 6 are driven by the power from the engine 8. May be.

  In the above-mentioned [Best Mode for Carrying Out the Invention], [First Alternative Embodiment of the Invention] and [Second Alternative Embodiment of the Invention], a mower employing the engine 8 as the prime mover E is provided. As shown in the example, a different configuration may be adopted as the driving part E, for example, an electric motor (not shown) driven by electric power such as a battery or a commercial power source may be adopted instead of the engine 8.

  In the above-mentioned [Best Mode for Carrying Out the Invention], [First Alternative Embodiment of the Invention] and [Second Alternative Embodiment of the Invention], the engine 8 is connected to the upper portion of the transmission case 7 in an interlocking manner. However, a driving part E (not shown) in which the transmission case 7 and the engine 8 are integrally formed may be employed. Further, for simplicity, the transmission case 7 may be omitted, and the driving part E may be configured by only the engine 8 (not shown). In this case, the drive shaft and the swinging support shaft extending in the left-right direction from the engine 8 to the traveling device (wheels and the like) are extended, and the downward transmission shaft from the lower portion of the engine 8 to the cutting blade 10 is extended. The body frame 2 is supported so as to be swingable around the left and right axis (not shown).

1 traveling body 5 front wheel (traveling device)
6 Rear wheels (travel device)
7a Drive shaft 7b Oscillating support shaft 10 Cutting blade 90 Cutting height adjustment mechanism (tilt angle adjustment mechanism)
E Driving part P1 shaft center (left and right shaft center)
P2 axis (vertical axis)
α Forward descending tilt angle, backward descending tilt angle

Claims (3)

In a walking type mower having a driving unit, a driving unit that is rotated by power from the driving unit, and a cutting blade.
The cutting blade is supported at the lower part of the driving part so as to be rotatable around a vertical axis, and the driving part and the cutting blade are supported on the traveling machine body so as to be swingable around a left and right axis,
In the state where the traveling device is in contact with the grounding surface, the cutting blade is supported by the traveling machine body without the grounding contact with the grounding surface,
A tilt posture changing mechanism for changing the posture of the prime mover and the cutting blade to a forward downward tilt posture in which the front side of the cutting blade swings downward and a rear downward tilt posture in which the rear side of the cutting blade swings downward; Equipped with a walking mower.   The walking mower according to claim 1, wherein the traveling device includes left and right front wheels and left and right rear wheels supported by the traveling machine body.   The walking mower according to claim 1 or 2, wherein a steering handle is provided on the traveling machine body.

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