JP2005137271A - Walking type mower - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a walking type mower with which traveling wheels are suitably decelerated and driven without causing a bad condition by adhesion and deposition of reaped weeds. <P>SOLUTION: In this walking type mower with which the traveling wheels 4 are mounted on the circumferential part of a mowing part 3 equipped with reaping blades 2 to be rotated and driven in a reaping blade housing 1 and a motive power part 5 for driving the reaping blades 2 and the traveling wheels 4 is loaded on the upper part of the mowing part 3, a recessed space 62 opened toward the inside of a machine body is formed in the inside of the traveling wheels 4, a deceleration mechanism 61 for decelerating and driving the traveling wheels 4 is housed in the recessed space 62 and the opening of the recessed space 62 is closed by a member that supports the deceleration mechanism 61 and is fixed to the machine body side. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a walking type mower used for weed cutting on a shore.

As the walking type mower, a driving wheel is provided on the periphery of the mowing unit provided with a cutting blade that is driven to rotate in the cutting blade housing, and the cutting blade and the driving wheel are driven above the mowing unit. There is known a device equipped with a section (see, for example, Patent Document 1).
JP 2001-238514 A

  In a walking type mower, it is necessary to greatly reduce the high speed power from the driving part to a speed that can follow the walking and transmit it to the traveling wheel, and in general, a speed reducing means will be incorporated in the traveling transmission system, After decelerating in the transmission case, it is transmitted to a speed reduction case with a built-in chain speed reduction mechanism, and the traveling wheels pivotally supported on the free end of the speed reduction case are driven to decelerate.

  Here, the deceleration case will be arranged side by side inside the body of the traveling wheel, and the mowing grass leaked from the cutting blade housing due to the mowing operation or the grass cut up by the lug of the traveling wheel will decelerate. It tends to adhere and accumulate on the case, and as deposition progresses, grass may get caught between the traveling wheel and the chain case, which may increase rotational frictional resistance acting on the traveling wheel and reduce traveling performance. At this point, the worker had to remove the grass that had adhered and accumulated.

  The present invention has been made paying attention to such points, and has as its main object to provide a walking-type grass mower that can suitably drive the traveling wheels at a reduced speed without causing problems due to the adhesion and accumulation of mowing grass. .

1st invention equips a cutting wheel with the driving | running | working wheel in the surrounding part of the mowing part provided with the cutting blade rotationally driven in a cutting blade housing, and drives the said cutting blade and a driving | running | working wheel to the upper part of the said mowing part. A walking-type mower with a part,
A recessed space opened toward the inside of the machine body is formed inside the traveling wheel, and a deceleration mechanism that drives the traveling wheel 4 to decelerate is accommodated in the recessed space. The opening of the recessed space is closed by a fixed member.

  According to the above configuration, there is no dedicated deceleration case inside the vehicle body of the traveling wheel, so to speak, the traveling wheel itself and the member on the vehicle body side that closes the opening of the recessed space function as a deceleration case that houses the deceleration mechanism. Become.

  Therefore, according to the first invention, since there is no dedicated speed reduction case in parallel with the traveling wheel, there is no phenomenon in which accumulated mowing grass is caught between the speed reduction case and the traveling wheel, and frequent cleaning operations are not performed. Also, the traveling wheel can be driven at a reduced speed.

  According to a second aspect, in the first aspect, a member that closes the opening of the recessed space is provided with an openable / closable inspection port.

  According to the above configuration, the body-side member that closes the opening of the recessed space and the traveling wheel are arranged in sliding contact or in close proximity to prevent cutting grass and soil from entering the recessed space. During long periods of use, small dust and dirt will enter the recessed space, so you can open the inspection port and clean it in a timely manner. The inspection port is also used to supply lubricating oil to the accommodated reduction mechanism.

  Therefore, according to the second invention, the above-described effects of the first invention are brought about, and the maintainability is excellent, and the practical convenience is high.

  According to a third invention, in the first or second invention, the traveling wheel includes a plurality of propulsion lugs and a rectilinear plate having a circular outer peripheral edge.

  According to the above configuration, when mowing while running along a slope on the shore along the contour line, the propulsion lug that is provided intermittently in the circumferential direction on the outer periphery of the wheel reliably catches the slope, and sufficient propulsive force is provided. Demonstrated. In addition, the straight running plate continuously provided in the circumferential direction on the outer periphery of the wheel will bite into the slope to prevent the lateral displacement of the aircraft, and reliably and smoothly follow the contour lines without applying a large force to the aircraft operation It can be run. If the height of the propulsion lug is set to be the same as or slightly lower than the height of the rectilinear plate, it is possible to travel on a paved road without vibration.

  Therefore, according to the third invention, the above-mentioned effects of the first or second invention are brought about, and grass cutting along the contour line on the slope can be easily performed, and the maneuverability is excellent. Become.

  FIG. 1 shows the entire side surface of the walking mower according to the present invention, and FIG. 2 shows the entire plane. This walking type mower is equipped with traveling wheels 4 on the front, rear, left and right of a cutting blade 3 provided with a cutting blade 2 that is driven to rotate about a longitudinal axis P inside the cutting blade housing 1, and the mowing portion 3. The engine 5 is mounted as a driving part for driving the cutting blade 2 and the traveling wheel 4 at the central part of the, and the steering handle 6 whose direction can be changed is extended from the mowing part 3.

  The mowing unit 3 is provided with a pair of left and right main frames 10 formed by bending a plate material downwardly in a U-shape, and a drive case 12 is mounted on a stay 11 that extends between the front and rear intermediate portions of the left and right main frames 10. Are coupled and supported, and the engine 5 is mounted on an upper portion of the drive case 12.

  The engine 5 is a recoil start type vertical air-cooled gasoline engine, and its downward output shaft 5a and the input shaft 13 arranged on the upper side of the drive case 12 are connected to each other in a concentric manner via a centrifugal clutch 14. In addition, the input shaft 13 is equipped with a brake 15.

  As shown in FIG. 9, cylindrical support shafts 16 are rotatably supported horizontally at the front and rear ends of the left and right main frames 10, and the traveling arms are fixed to the support arms 17 fixed to the left and right ends of each cylindrical support shaft 16. An axle 18 to which the wheels 4 are connected is rotatably supported, and the front, rear, left and right traveling wheels 4 are synchronously driven forward or reversely as described later.

  Next, the transmission structure in the drive case will be described with reference to FIGS.

  A second shaft 21 is provided on the rear side of the input shaft 13 in the drive case 12, and a gear G 1 formed integrally with the lower end portion of the input shaft 13 and a gear G 2 key-connected to the upper half portion of the second shaft 21; Is coupled to the lower half of the second shaft 21, and a shift gear G <b> 3 is slidably fitted on the lower half portion of the second shaft 21 in an upward biased state by a spring 22. Further, below the input shaft 21, a cutting blade driving shaft 23 with the cutting blade 2 mounted on the lower end is disposed so as to be relatively rotatable, and a gear G4 connected to the cutting blade driving shaft 23 is connected to the shift gear G3. Always bite.

  The shift gear G3 constitutes a cutting blade clutch 24 that intermittently transmits power to the cutting blade drive shaft 23. The shift gear G3 is biased upward and engaged with the internal teeth 25 of the gear G2. “Clutch disengagement” in which the transmission to the cutting blade drive shaft 23 is cut off by shifting the gear G3 downward against the spring 22 and disengaging it from the internal teeth 25. A state is brought about. The shift gear G3 is engaged with a shift fork 27 that is swing-operated by the clutch operation shaft 26, and the operation lever 28 connected to the outer end of the case of the clutch operation shaft 26 is engaged with the lever guide 29. It is possible to hold the cutting blade clutch 24 energized and pressed in the “clutch disengaged” state.

  A third shaft 31 is provided upright on the right side of the input shaft 13 and the second shaft 21, and a pair of front and rear traveling output shafts 32a and 32b are provided on the right side of the case so as to protrude horizontally. A traveling high / low speed change mechanism 33 is provided on the third shaft 31, and a forward / reverse switching mechanism 34 is provided on both the output shafts 32a and 32b.

  The high / low speed changing mechanism 33 includes two large and small gears G5 and G6 that are key-connected to the second shaft 21, and two transmission gears G7 and G8 that are engaged with these gears and loosely fitted to the third shaft 31. The third shaft 31 is shifted in two steps of high and low by integrating one of the transmission gears G7 and G8 with the third shaft 31 as follows.

  In other words, the speed change operation shaft 35 is slidable up and down and is fitted in the upper biased state by the internal spring 36 inside the third shaft 31, and the drive pin 37 penetratingly connected to the speed change operation shaft 35 is provided in the first shaft 31. Projected outwardly from the upper and lower elongated holes 38 formed in the three shafts 31 and selectively engaged with the engagement grooves 39 formed in the inner periphery of the gear transmission gears G7 and G8. The shaft 35 is slid upward to integrate the large-diameter transmission gear G8 and the third shaft 31 so that the third shaft 31 is driven at a low speed, and the transmission operation shaft 35 is slid downward to reduce the small-diameter transmission gear G7. The third shaft 31 is driven at a high speed by integrating the third shaft 31 with the third shaft 31. The speed change operation shaft 35 is slid by a vertical swing operation of the speed change lever 40.

  The forward / reverse switching mechanism 34 is configured to be able to selectively extract the rotational powers in the rotational direction which are opposite to each other from the pair of front and rear traveling output shafts 32a and 32b protruding to the right side of the case. Forward / reverse switching is performed by transmitting power to the traveling wheels 4.

  In other words, the traveling output shafts 32 a and 32 b are arranged at positions spaced apart from each other by an equal distance from the axial center of the third shaft 31, and the worm gear 41 that is externally fitted and fixed to the lower half of the third shaft 31. Further, a pair of worm wheels 42 loosely supported by the traveling output shafts 32a and 32b are respectively engaged from the front and the rear, and the worm gears 41 are decelerated greatly in directions opposite to each other by rotation of the worm gear 41 in a fixed direction. Are driven to rotate.

  The front traveling output shaft 32a has a forwardly driven worm wheel 42 and a forward clutch 43a connecting the output shaft 32a. The rear traveling output shaft 32b is reversely driven. A reverse clutch 43b for connecting the worm wheel 42 and the output shaft 32b is provided.

  These clutches 43a and 43b are "engaged with clutch" by energizing and shifting the clutch member 44, which is splined to the traveling output shafts 32a and 32b, by a spring 45 and engaging and connecting to the worm wheel 42 from the side surface. The clutch 44 is reversely shifted against the spring 45 to release the engagement with the worm wheel 42, so that "clutch disengagement" is established, and the engagement claw 44a formed at the end of the clutch member 44 has a worm wheel. The head 46 of the bolt 46 screwed on the side face 42 is engaged from the circumferential direction. The worm wheel 42 is formed by cutting a copper alloy so as to be smoothly engaged and driven by the worm gear 41. In order to increase the engagement strength and durability with the clutch member 44, the engagement claw The heads 44a and 46 are quenched.

  The operation shaft 48 of each shift fork 47 for operating the clutch member 44 in the forward clutch 43a and the reverse clutch 43b is a single forward / reverse switching lever provided swingably around the fulcrum p near the tip of the steering handle 6. 49 is connected to each other via a wire 50, and the clutch 50 is brought into a clutch engagement state when the wire 50 is loosened, and the clutch disengagement state is brought about when the wire 50 is pulled beyond a predetermined amount. ing. Here, both the wires 50 are distributed to the left and right of the fulcrum p and connected to the forward / reverse switching lever 49, and both the wires 50 are operated in a contradictory manner by swinging the forward / backward switching lever 49.

  According to the above configuration, when the forward / reverse switching lever 49 is operated to the “forward” position and is latched and held by the lever guide 51, the wire 50 corresponding to the forward clutch 43a is loosened and the forward clutch 43a is engaged. When the wire 50 corresponding to the reverse clutch 43b is greatly pulled and the reverse clutch 43b is disconnected, and when the forward / reverse switching lever 49 is operated and held in the "reverse" position, it corresponds to the forward clutch 43a. Then, the forward clutch 43a is disengaged, the wire 50 corresponding to the reverse clutch 43b is loosened and the reverse clutch 43b is inserted, and the forward / reverse switching lever 49 is further moved to the "neutral" position. When operated and locked, the forward clutch 43a and the reverse clutch 43b are pulled together by the wires 50, A cut-off state is brought about, and by operating to this “neutral” position, power transmission to the traveling system can be cut off and the traveling wheel 4 can be put into a free-wheeling state. It can be moved. Further, the engine is started when the forward / reverse switching lever 49 is switched to the “neutral” position.

  Sprockets 55a and 55b are attached to the outer ends of the traveling output shafts 32a and 32b, respectively, and a sprocket 57 is also attached to the right end of the transmission shaft 56 inserted and supported by the cylindrical support shaft 16 at the front and rear ends of the main frame. The chain 58 is wound around the sprockets 55 a, 55 b, 57 in a series, and is stretched without loosening via the tie toner 59 and the tension roller 60.

  The left and right ends of the transmission shaft 56 and the axle 18 are linked and connected by a gear reduction mechanism 61. The gear reduction mechanism 61 is configured by engaging a small-diameter gear G9 connected to the end of the transmission shaft 56 and a large-diameter gear G10 connected to the axle 18, and the entire gear reduction mechanism 61 is The recessed space 62 is housed in a recessed space 62 formed inside the traveling wheel 4, and the opening of the recessed space 62 is closed by a fixed member that supports the gear reduction mechanism 61.

  As shown in FIGS. 11 and 12, the traveling wheel 4 is configured as a sheet metal press wheel having a recessed space 62 facing the inside of the machine body, and a disc-shaped lid 63 attached to the support arm 17. The outer peripheral flange portion is disposed so as to be sufficiently close to or slidably contact the inner periphery of the recessed space 62, so that the inward opening of the recessed space 62 is closed. In addition, an inspection port 65 that can be opened and closed by a removable cover 64 is formed at an appropriate position of the lid 63 so that foreign matter that has entered the recessed space 62 can be discharged and removed arbitrarily. Yes. Further, a rectilinear plate 66 having a circular outer peripheral edge is integrally extended in a flange shape on the outer periphery of the traveling wheel 4, and propulsion lugs 67 formed by bending and erecting both ends of the metal strip are projected at a constant pitch in the circumferential direction. ing. Note that the propulsion lug 67 protrudes at the same height as the outer peripheral diameter of the rectilinear plate 66, or slightly lower than that, so that traveling vibration is less likely to occur when traveling on flat ground. In addition, a shear pin is used for the connecting pin 18a between the traveling axle 18 and the wheel hub 4a. When an excessive traveling load is applied, the connecting pin 18a is broken, and damage to the traveling transmission system is avoided. Yes.

  An operating arm portion 17a refracted from the base of the front and rear support arms 17 positioned on the left side and a cutting height adjustment lever 68 erected on the right side of the central portion of the mowing portion 3 so as to swing back and forth are linked rods. 69, the cutting height adjusting lever 68 is swung back and forth, whereby the front and rear and left and right support arms 17 rotate together with the cylindrical support shaft 16 so that all traveling wheels 4 are in the same direction. The height of the cutting blade 2 with respect to the ground, that is, the cutting height can be changed by raising and lowering by the same amount. In this example, the four locking portions formed with the cutting height adjusting lever 68 on the fixed lever guide 70 It is possible to change the cutting height into four stages by selecting and engaging in.

  The cutting blade housing 1 constituting the mowing unit 3 includes front and rear top plates 71 attached to the left and right main frames 10, left and right cutting blade covers 72 projecting laterally outward from the main frame 10, and a top plate. 71 is configured to cover the cutting blade rotation trajectory with rubber drooping covers 73 attached to the front and rear ends of 71, and the left and right cutting blade covers 72 have dimensions corresponding to the replacement or cutting blade diameter when damaged. A bolt is detachably connected to the main frame 10 so that it can be replaced.

  As shown in FIGS. 15 and 16, the cutting blade 2 is provided on the upper and lower surfaces at four circumferential positions on a disc-shaped cutting blade support plate 74 connected and fixed to the cutting blade drive shaft 23. Is pivotally connected around a fulcrum q parallel to the rotational axis of the blade so that the cutting blade 2 can swing backward when it acts on a stone or a hard foreign object on the ground. Each cutting blade 2 is formed by forming a pivot connection hole and a cutting edge on a cutting blade material of the same specification formed by refracting a band plate material at a predetermined angle, and is attached to the upper surface of the cutting blade support plate 74. The cutting blade 2 is attached in a posture in which the cutting action portion is refracted upward, and the cutting blade 2 mounted on the lower surface of the cutting blade support plate 74 is attached in a posture in which the cutting action portion is refracted downward. The grass is shredded by alternately arranging the cutting blades 2 having different cutting heights in the circumferential direction. Further, an anti-winding drum 75 is attached to the upper surface of the cutting blade support plate 74, and blades 76 for discharging the mowing grass are attached in a substantially radial manner, so that the mowing grass is diffused and left in the passage marks of the mowing portion 3. It has become so. A disc-shaped guide cover 77 is fixed to the ceiling portion in the cutting blade housing 1.

  The steering handle 6 is configured by connecting a loop handle portion 6b to a free end of a handle body 6a made of a round pipe material, and on the right side of the engine (driving portion) 5, front and rear traveling wheels. 4 is extended in a cantilevered manner from a low position close to the upper surface of the cutting blade housing 1 at a position close to the middle position of 4, and can be adjusted to change its direction around the vertical axis x and up and down around the horizontal axis y. It is configured to be swing adjustable. As shown in FIG. 20, the loop handle portion 6b is mounted so as to be adjustable within the angle range of the long hole 81 around the horizontal axis z, and is fixed at an arbitrary angle by tightening the set bolt 82. It can be done.

  As shown in FIGS. 17 and 18, the stay 11 fixed to the right main frame 10 is provided with a vertical boss 83, and the handle fulcrum 84 formed of a cylindrical shaft can be rotated from above the vertical boss 83. And is supported by a pin 85 attached to the downward projecting portion. A flange 86 is fixed to the outer periphery of the upper and lower intermediate portions of the handle support shaft 84, and this flange 86 is received and placed on a circular support plate 87 provided continuously with the upper end of the vertical boss 83. A lateral boss 88 constituting the lateral axis y is fixed to the upper end of the handle support shaft 84, and the base end of the steering handle 6 is pivotally connected to the lateral boss 88 so as to be swingable up and down.

  A pivot lock pin 90 supported via a boss 89 is attached to the flange 86 so that the pivot lock pin 90 can be withdrawn and retracted below the flange, and the pivot lock pin 90 is engaged in a predetermined circumferential direction of the support plate 87. A plurality of lock holes 91 are provided to support the steering handle 6 together with the handle support shaft 84 and the vertical axis x by pulling the turning lock pin 90 upward against the lock biasing spring 92 built in the boss 89. The swivel lock pin 90 can be urged and moved downward at a desired swivel position and engaged with the lock hole 91 so that the steering handle 6 can be swiveled and fixed at that position. The steering handle 6 can be reoriented within a predetermined range from the backward posture shown in FIG. 1 to the forward posture. Note that the direction change range is limited by the contact between the stopper pin 93 protruding from the support plate 87 and the end of the flange 86.

  Further, a oscillating lock pin 95 is mounted on a boss 94 provided on the lower surface near the base of the handle body 6a in a protruding and urged state toward the horizontal axis y, and the flange 86 is centered on the horizontal axis y. A lock plate 96 curved in a circular arc shape is fixed, and a plurality of lock holes 97 for engaging and supporting the oscillating lock pin 95 urged and protruded are provided in the lock plate 96 at an appropriate pitch in the vertical direction. The steering handle 6 can be swung up and down around the y axis of the horizontal axis by retracting the rocking lock pin 95 against the internal spring 98 and pulling it out of the lock hole 97. The steering handle 6 can be fixed at the height position by causing the rocking lock pin 95 to be biased and projecting into the lock hole 97. The upward swing of the steering handle 6 is limited by the contact between the stopper portion 96a formed at the upper end of the lock plate 96 and the boss 94.

  20 and 21, a pair of grip levers 100 and 101, a turning lock pin 90, and a swinging lock pin 95 provided on the left and right of the steering handle 6 near the base of the loop handle portion 6b are operated. They are linked by the wires 102 and 103, and by operating the grip levers 100 and 101 together with the base of the loop handle portion 6b and pulling the operation wires 102 and 103, the swing lock pin 90 or the swing lock pin 95 is operated. The swing lock or the swing lock can be released by pulling out and retreating, and after releasing the lock, the steering handle 6 is continuously held and the direction or height is arbitrarily changed, and the desired turning direction or The handle can be locked by releasing the grip levers 100 and 101 at a height. It is.

  The loop handle portion 6b of the steering handle 6 is provided with a gate-shaped accelerator lever 105 that can swing up and down around a fulcrum r and is biased upward. Two operation wires 106 and 107 are extended from the base portion of the accelerator lever 105, and one operation wire 106 is linked to a speed control mechanism (not shown) provided in the engine 5 and the other operation is performed. Wires 107 are linked to the brakes 15 respectively. Then, the accelerator lever 105 is pulled down and rocked against the upward biasing force and is gripped together with the loop handle portion 6b, thereby pulling both the operation wires 106 and 107 together to increase the rotational speed of the engine 5 (accelerator). When the engine speed increases, the centrifugal clutch 14 is actuated and power is transmitted to the input shaft 13 to enable driving and cutting blade driving. Further, when the grip of the accelerator lever 105 is released, the accelerator lever 105 returns and swings upward, the engine 5 is rotated down to the idling (accelerator down), the centrifugal clutch 14 is disengaged, and the power to the traveling system and the cutting blade drive system is released. The transmission is cut off and the input shaft 13 is braked by the operation of the brake 15 so that the inertial rotation of the cutting blade 2 is promptly stopped.

  The mower is configured as described above, and when cutting weeds on a slope such as a farm road, as shown in FIG. 3, the mowing unit 3 is positioned on the slope in a posture along the contour line, and is operated. The handle 6 is turned and fixed in the lateral direction toward the farm road, and in this state, the mowing unit 3 is moved forward or backward along the contour line. On a wide slope with a large length in the inclination direction, the traveling position is set to the position of the slope by repeatedly pushing back and forth on the steering handle 6 or pulling up the slope. It will be shifted in the tilt direction.

  As described above, when the steering handle 6 is turned sideways, the forward direction and the reverse direction with respect to the aircraft may not be known. Therefore, the lever guide 108 of the forward / reverse switching lever 49 is attached to the front and rear ends of the mowing unit 3. It is preferable to display the forward position and the reverse position with a color corresponding to the color mark.

  Further, in this mower that is often used on a slope, the fuel tank 109 is provided so as to be positioned on the lower slope, and the replenishing port 110 is provided in a direction toward the upper slope. Further, in order to make it easier for an operator on the slope to start the recoil start of the engine 5 from the upper side of the slope, the start knob 111 located on the rear side of the engine 5 is located on the left side where the base of the steering handle 6 is installed. It is provided so that it can be pulled.

  In addition, this invention can also be implemented with the following forms.

  (1) The driving part mounted and arranged on the upper part of the mowing part 3 can also be comprised with an electric motor.

  (2) As the speed reduction mechanism built in the traveling wheel 4, in addition to using the gear speed reduction mechanism 61 as described above, the chain extends over a small diameter sprocket fixed to the transmission shaft 56 and a large diameter sprocket fixed to the axle 18. It is also possible to use a chain speed reduction mechanism that is wound around the shaft.

  (3) In the above embodiment, the lid 63 attached to the support arm 17 that pivotally supports the traveling wheel 4 is used as a member on the machine body that closes the opening of the recessed space 62 formed in the traveling wheel 4. If the arm 17 is made of aluminum die cast, the support arm 17 itself can be shaped to close the opening.

Overall side view of walking mower Overall plan view of the walking type mower Front view showing the state of mowing on the slope Longitudinal front view of drive case Longitudinal front view of main part showing cutting blade clutch disengagement state Longitudinal side view showing high and low speed change mechanism Cross-sectional plan view of the forward / reverse switching mechanism Plan view of the forward / reverse switching operation section Plan view showing airframe structure and running section Side view showing the running section Cross-sectional plan view showing wheel drive structure Longitudinal side view of traveling wheel Top view of the blade housing Exploded perspective view of cutting blade housing Side view of the main part of the mowing section Top view of the cutting blade Vertical side view showing the attitude adjustment structure of the steering handle Plan view showing the attitude adjustment structure of the steering handle Vertical section of swivel lock structure Longitudinal side view showing the operating part of the steering handle Plan view showing the operating part of the steering handle Front view of forward / reverse switching operation section

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Cutting blade housing 2 Cutting blade 3 Grass cutting part 4 Traveling wheel 5 Driving part (engine)
61 Deceleration mechanism 62 Recessed space 63 Member (lid)
65 Inspection port 66 Straight plate 67 Propulsion lug

Claims (3)

The cutting blade housing is provided with a traveling wheel on the periphery of the mowing portion provided with a cutting blade that is driven to rotate, and the driving portion that drives the cutting blade and the traveling wheel is mounted on the upper portion of the mowing portion. A walking mower,
A recessed space opened toward the inside of the machine body is formed inside the traveling wheel, and a deceleration mechanism that drives the traveling wheel 4 to decelerate is accommodated in the recessed space. A walking mower characterized in that an opening of the recessed space is closed by a fixed member.   The walking mower according to claim 1, wherein an inspection port that can be opened and closed is provided in a member that closes the opening of the recessed space.   The walking mower according to claim 1 or 2, further comprising a plurality of propulsion lugs and a rectilinear plate having a circular outer peripheral edge on an outer peripheral portion of the traveling wheel.

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