JP6238749B2 - Walking mower - Google Patents

Description

  The present invention relates to a walk-type mowing provided with a cutting blade that is driven to rotate around a vertical axis, a cutting blade housing that houses the cutting blade, an engine provided on the upper portion of the cutting blade housing, and a traveling wheel. Related to the machine.

Some walking mowers have a structure as disclosed in Patent Document 1 in order to transmit engine power to a cutting blade and wheels.
In Patent Document 1, an output shaft extends downward from an engine provided in an upper portion of a cutting blade housing, a cutting blade driving shaft connected to the cutting blade extends upward, and the output shaft and the cutting blade driving shaft are extended. Are arranged in parallel, a gear mechanism having a flat gear is provided across the output shaft and the cutting blade drive shaft, and the power of the output shaft is transmitted to the cutting blade drive shaft through the gear mechanism. The
A traveling transmission shaft that transmits power to the wheels is disposed sideways so as to intersect the cutting blade drive shaft, and a worm gear mechanism is provided across the cutting blade drive shaft and the traveling transmission shaft so that the power of the cutting blade drive shaft is It is transmitted to the travel transmission shaft through the worm gear mechanism.

JP 2009-38987 A (see FIG. 10)

In the structure of Patent Document 1, since the output shaft, the gear mechanism, the cutting blade drive shaft, the worm gear mechanism, and the traveling transmission shaft are arranged in order, the support case that accommodates these is relatively large. . Thereby, there is room for improvement in terms of size reduction and weight reduction of the support case.
An object of the present invention is to provide a compact transmission system that transmits engine power to a cutting blade and wheels in a walking mower, and accommodates a transmission system that transmits engine power to the cutting blade and wheels. The object is to reduce the size and weight of the support case.

[I] (Configuration)
The first feature of the present invention is that the walking mower is configured as follows.
A cutting blade that is driven to rotate around a vertical axis, a cutting blade housing that houses the cutting blade, another cutting blade that is located next to the cutting blade housing, and an upper portion of the cutting blade housing. An engine and traveling wheels,
An output shaft that transmits power of the engine and that extends downward, and a cutting blade drive shaft that is connected to the cutting blade and extends upward are arranged in parallel,
A gear mechanism having a flat gear is provided across the output shaft and the cutting blade drive shaft, and the power of the output shaft is transmitted to the cutting blade drive shaft via the gear mechanism,
A cutting blade transmission shaft that transmits the power of the cutting blade drive shaft to the other cutting blade is disposed sideways in a state of being positioned on one side with respect to the cutting blade drive shaft in the left-right direction of the machine body,
A traveling transmission shaft that transmits power to the wheels is disposed laterally so as to intersect the output shaft in a state where the traveling transmission shaft is located on the opposite side of the cutting blade drive shaft with respect to the cutting blade drive shaft in the horizontal direction of the machine body. A worm gear mechanism is provided across the output shaft and the travel transmission shaft, and the power of the output shaft is transmitted to the travel transmission shaft via the worm gear mechanism.

(Operation and effect of the invention)
In the structure of Patent Document 1, an output shaft (62 in FIG. 10 in Patent Document 1), a gear mechanism (64 and 72 in FIG. 10 in Patent Document 1), a cutting blade drive shaft (65 in FIG. 10 in Patent Document 1), The worm gear mechanism (73 and 75 in FIG. 10 of Patent Document 1) and the traveling transmission shaft (74 in FIG. 10 of Patent Document 1) are arranged in order, and the output shaft (62 in FIG. 10 of Patent Document 1). There is a space below.

On the other hand, according to the first feature of the present invention, the output shaft, the gear mechanism and the cutting blade drive shaft are arranged in order, but the worm gear mechanism and the traveling transmission shaft are arranged at the position of the output shaft, The power of the output shaft is transmitted to the travel transmission shaft via the worm gear mechanism, and is not disposed on the lateral outer side (opposite side of the output shaft) of the cutting blade drive shaft.
Therefore, according to the first feature of the present invention, by using the space in the vicinity of the output shaft generated in the structure of Patent Document 1 as a space for arranging the worm gear mechanism and the traveling transmission shaft, the power of the engine is increased. The transmission system that transmits to the cutting blade and the wheel can be configured compactly. When a support case that houses a transmission system that transmits engine power to the cutting blades and wheels is provided, the support case can be reduced in size and weight.

[II] (Configuration)
The second feature of the present invention resides in the following configuration in the walking mower of the first feature of the present invention.
The output shaft is provided with the gear mechanism and the worm gear mechanism so that the worm gear mechanism is positioned at an upper and lower position below the gear mechanism.

(Operation and effect of the invention)
If the worm gear mechanism is configured to be positioned at the upper and lower positions below the gear mechanism as in the second feature of the present invention, the position of the traveling transmission shaft connected to the worm gear mechanism can be set low. Along with this, the position of the transmission system connected from the traveling transmission shaft to the wheel can also be set low, so that the overall size of the walking type mower can be reduced and the center of gravity can be lowered.

[III] (Configuration)
The third feature of the present invention resides in the following configuration in the walking mower.
A cutting blade that is rotationally driven around a vertical axis, a cutting blade housing that houses the cutting blade, an engine provided on an upper portion of the cutting blade housing, and a traveling wheel.
An output shaft that transmits power of the engine and that extends downward, and a cutting blade drive shaft that is connected to the cutting blade and extends upward are arranged in parallel,
A gear mechanism having a flat gear is provided across the output shaft and the cutting blade drive shaft, and the power of the output shaft is transmitted to the cutting blade drive shaft via the gear mechanism,
A travel transmission shaft that transmits power to the wheels is disposed laterally so as to intersect the output shaft, and a worm gear mechanism is provided across the output shaft and the travel transmission shaft, and the power of the output shaft is Transmitted to the travel transmission shaft through a worm gear mechanism,
The output shaft is provided with the gear mechanism and the worm gear mechanism so that the worm gear mechanism is positioned at a vertical position below the gear mechanism,
Next to the cutting blade housing, another cutting blade and another cutting blade housing that houses the another cutting blade,
The cutting blade drive shaft is provided with a first bevel gear at a lower vertical position on the lower side of the traveling transmission shaft, and a cutting blade transmission shaft for transmitting power to the other cutting blade is provided with the gear mechanism and the first Place it sideways so that it is positioned up and down with the bevel gear,
A second bevel gear provided on the cutting blade transmission shaft is engaged with the first bevel gear, and the power of the cutting blade drive shaft is transmitted to the cutting blade transmission shaft via the first and second bevel gears.

(Operation and effect of the invention)
In the structure of Patent Document 1, an output shaft (62 in FIG. 10 in Patent Document 1), a gear mechanism (64 and 72 in FIG. 10 in Patent Document 1), a cutting blade drive shaft (65 in FIG. 10 in Patent Document 1), The worm gear mechanism (73 and 75 in FIG. 10 of Patent Document 1) and the traveling transmission shaft (74 in FIG. 10 of Patent Document 1) are arranged in order, and the output shaft (62 in FIG. 10 of Patent Document 1). There is a space below.
On the other hand, according to the third feature of the present invention, the output shaft, the gear mechanism and the cutting blade drive shaft are arranged in order, but the worm gear mechanism and the traveling transmission shaft are arranged at the position of the output shaft, The power of the output shaft is transmitted to the travel transmission shaft via the worm gear mechanism, and is not disposed on the lateral outer side (opposite side of the output shaft) of the cutting blade drive shaft.
Therefore, according to the third feature of the present invention, by using the space in the vicinity of the output shaft generated in the structure of Patent Document 1 as a space for arranging the worm gear mechanism and the traveling transmission shaft, the power of the engine is increased. The transmission system that transmits to the cutting blade and the wheel can be configured compactly. When a support case that houses a transmission system that transmits engine power to the cutting blades and wheels is provided, the support case can be reduced in size and weight.
Further, as in the third feature of the present invention, when the worm gear mechanism is positioned at the upper and lower positions below the gear mechanism, the position of the traveling transmission shaft connected to the worm gear mechanism can be set low. Along with this, the position of the transmission system connected from the traveling transmission shaft to the wheel can also be set low, so that the overall size of the walking type mower can be reduced and the center of gravity can be lowered.
Further, in the walking type mower , in addition to the one-side cutting type having one cutting blade and a cutting blade housing as in Patent Document 1, two cutting blade housings (cutting blades) are arranged side by side in the left-right direction. There is a cutting type.

  According to the third aspect of the present invention, in the two-sided mower type walking mower as described above, the power of the cutting blade drive shaft is transmitted to another cutting blade via the cutting blade transmission shaft. The gear mechanism is positioned at the upper and lower positions on the upper side of the travel transmission shaft, whereas the first bevel gear is positioned at the upper and lower positions on the lower side of the travel transmission shaft and between the gear mechanism and the first bevel gear. The travel transmission shaft is positioned at the vertical position, and the travel transmission shaft, the gear mechanism, and the first bevel gear are compactly arranged.

Similarly, according to the third aspect of the present invention, the cutting blade transmission shaft, the gear mechanism, and the second bevel gear are arranged in a compact manner by positioning the cutting blade transmission shaft in the vertical position between the gear mechanism and the first bevel gear. The
Further, the traveling transmission shaft is positioned at the vertical position between the gear mechanism and the first bevel gear, and the cutting blade transmission shaft is positioned at the vertical position between the gear mechanism and the first bevel gear, so that the traveling transmission shaft and the cutting shaft are disposed. Since the blade transmission shaft is positioned at the same vertical position, this is advantageous in terms of compactness.

  As described above, according to the third feature of the present invention, the traveling transmission shaft is positioned at the vertical position between the gear mechanism and the first bevel gear, and the cutting blade transmission is at the vertical position between the gear mechanism and the first bevel gear. The transmission system for transmitting the engine power to the cutting blade and the wheel can be made compact by the point where the shaft is located and the point where the traveling transmission shaft and the cutting blade transmission shaft are located at the same vertical position. . When a support case that houses a transmission system that transmits engine power to the cutting blades and wheels is provided, the support case can be reduced in size and weight.

[IV] (Structure)
A fourth feature of the present invention resides in the following configuration in the walking mower of the third feature of the present invention.
A cutting blade clutch capable of transmitting and interrupting the power of the gear mechanism to the cutting blade drive shaft is provided at a connection portion between the gear mechanism and the cutting blade drive shaft.

(Operation and effect of the invention)
When the cutting blade clutch for driving and stopping the cutting blade is provided, according to the fourth feature of the present invention, the cutting blade clutch is provided at the connection portion between the gear mechanism and the cutting blade drive shaft, and the gear mechanism is operated by the cutting blade clutch. Power is transmitted to and cut off from the cutting blade drive shaft.
As a result, the cutting blade clutch is positioned at the same vertical position as that of the gear mechanism, and the traveling transmission is performed at the vertical position between the gear mechanism and the cutting blade clutch and the first bevel gear, as described in [III]. The shaft (cutting blade transmission shaft) is located, the traveling transmission shaft (cutting blade transmission shaft), the gear mechanism (cutting blade clutch) and the first bevel gear are arranged in a compact manner, and the engine power is supplied to the cutting blade and the wheel. The transmission system for transmitting to can be made compact. When a support case that houses a transmission system that transmits engine power to the cutting blades and wheels is provided, the support case can be reduced in size and weight.

It is a whole side view of a walk-type mower. It is a whole top view of a walking type mower. It is a top view of an engine and the 1st and 2nd cutting blade housing. It is a vertical side view of a 1st blade housing and a 1st support case. It is a transverse plane view of the 1st support case. FIG. 5 is a longitudinal front view of the first and second cutting blade housings and the first and second support cases in a state where the second cutting blade housing is held in a posture parallel to the first cutting blade housing. It is a vertical front view of the 1st and 2nd blade housing, and the 1st and 2nd support case in the state where the 2nd blade housing was changed in the downward direction from the posture parallel to the 1st blade housing. It is a top view of the 1st and 2nd cutting blade. It is the schematic which shows the work transmission system from an engine to the 1st and 2nd cutting blade, and the traveling transmission system from an engine to a rear wheel. It is a side view of the grip part of a left steering handle, a travel clutch lever, and an accelerator lever. It is a top view of the grip part of a left steering handle, a travel clutch lever, and an accelerator lever. It is a vertical rear view of the grip part of a left steering handle, a travel clutch lever, and an accelerator lever. It is a side view of a right steering handle and an operation lever. It is a top view of a right steering handle and an operation lever. It is a vertical rear view of a right steering handle and an operation lever.

[1]
As shown in FIGS. 1, 2, and 3, the first cutting blade housing 1 (corresponding to a cutting blade housing), the second cutting blade housing 2 (corresponding to another cutting blade housing), the first and second cutting blade housings 1. , 2, the first cutting blade 11 (corresponding to a cutting blade) and the second cutting blade 12 (corresponding to another cutting blade), the engine 3 supported on the upper portion of the first cutting blade housing 1, the first cutting blade A steering handle 4 connected to the blade housing 1, a first front wheel 5 (corresponding to a traveling wheel) and a rear wheel 7 (corresponding to a traveling wheel) supported by the first cutting blade housing 1, a second cutting blade A two-sided mower type walk-type mower is provided with second front wheels 6 (corresponding to traveling wheels) supported by the housing 2.

  As shown in FIGS. 1, 2, and 3, the first and second cutting blade housings 1 and 2 are configured by bending a sheet metal, and around the front and rear axis P <b> 1 adjacent to the left side of the first cutting blade housing 1. The second blade housing 2 is connected to be vertically changeable (swingable). A U-shaped support frame 13 is connected to the first cutting blade housing 1 and extends rearward in a plan view, and the rear wheel 7 is rotatably supported by a support bracket 13 a connected to the support frame 13. Yes.

  As shown in FIGS. 1, 2, and 3, a bifurcated support bracket 8 is connected to the front portions of the first and second cutting blade housings 1 and 2, and the bifurcated support bracket 8 has a bifurcated shape around the horizontal axis P <b> 2. A support arm 9 is supported so as to be swingable up and down, and the first and second front wheels 5 and 6 are rotatably supported by the support arm 9. A front cover 10 having a triangular shape in a side view extends forward from the front portions of the first and second cutting blade housings 1 and 2, and the support arm 9 and the first and second front wheels 5 and 6 are supported by the front cover 10. Is covered.

  As shown in FIGS. 1, 2, and 3, an operation lever 9 a connected to the support arm 9 extends through the front cover 10 and extends upward. By operating the operation lever 9a of the support arm 9 to change the angle of the support arm 9, and by engaging the operation lever 9a of the support arm 9 with the lever guide 10a of the front cover 10, the first and second The heights of the first and second front wheels 5 and 6 relative to the cutting blade housings 1 and 2 can be changed.

As described above, as shown in FIGS. 1, 2, and 3, the first and second front wheels 5, 6 with respect to the first and second cutting blade housings 1, 2 change the height of the first through the ground. And the attitude | position of the 2nd cutting blade housings 1 and 2 is changed, and the cutting height of the 1st and 2nd cutting blades 11 and 12 is changed.
A cover 69 located at the rear part between the first and second cutting blade housings 1 and 2 is connected to the left rear part of the first cutting blade housing 1, and the cut grass is attached to the first and second cutting blade housings 1 and 2. The cut grass is suppressed by the cover 69 so as not to scatter backwards from between.

[2]
Next, the support structure of the engine 3 will be described.
As shown in FIGS. 1, 3, 4, and 6, a support frame 13 is disposed on the back surface of the upper wall portion of the first cutting blade housing 1, and an L-shaped cross section is formed on the upper surface of the upper wall portion of the first cutting blade housing 1. Of the first cutting blade housing 1 between the support frame 13 and the connection bracket 14 by connecting the bolt 15 across the support frame 13 and the connection bracket 14. The support frame 13 and the connecting metal fitting 14 are connected to the first cutting blade housing 1 so as to sandwich.

As shown in FIGS. 1, 2, 3, 4, and 6, the first support case 21 is bolted to the connection fitting 14, and the first support case 21 is disposed on the upper surface of the first cutting blade housing 1. The engine 3 is connected to the upper surface of the first support case 21. The engine 3 has a cylinder case arranged horizontally so that the output shaft 3a faces downward, a centrifugal clutch 16 is connected to the output shaft 3a of the engine 3, and a boss portion 16a of the centrifugal clutch 16 is arranged downward. Yes.
The centrifugal clutch 16 is in a disconnected state when the engine 3 is idling, and is in a transmission state when the rotational speed of the engine 3 is higher than the idling state.

  As shown in FIGS. 4, 6, and 9, the transmission shaft 17 (which transmits engine power and corresponds to an output shaft extending downward) is rotatably supported by the first support case 21 in the vertical direction. The transmission shaft 17 is connected to the boss portion 16a of the centrifugal clutch 16 by a spline structure, and the output shaft 3a, the centrifugal clutch 16 (boss portion 16a) and the transmission shaft 17 of the engine 3 are arranged concentrically.

  As shown in FIG. 2, the center line CL in the front-rear direction passing through the left and right center of the first front wheel 5 and the left and right center of the rear wheel 7 is located at the left and right center of the first cutting blade housing 1 in plan view. The engine 3 (output shaft 3a) is arranged offset to the right side (opposite side of the second blade housing 2) with respect to the center line CL.

As shown in FIGS. 4, 6, and 9, the first cutting blade drive shaft 31 (corresponding to the cutting blade drive shaft) is supported by the first support case 21 so as to be vertically rotatable in parallel with the transmission shaft 17. The first cutting blade 11 is connected to the lower portion of the one cutting blade drive shaft 31.
As shown in FIG. 2, in plan view, the first cutting blade drive shaft 31 is arranged slightly to the left (second cutting blade housing 2 side) with respect to the center line CL, and the engine 3 (output shaft 3a) is The first cutting blade drive shaft 31 is disposed offset to the right side (opposite side of the second cutting blade housing 2).

[3]
Next, the traveling transmission system for the rear wheel 7 will be described.
A work transmission system that transmits the power of the engine 3 to the first and second cutting blades 11 and 12 from a lower transmission side of the centrifugal clutch 16 and a traveling transmission system that transmits the power of the engine 3 to the rear wheels 7 are arranged in parallel. The power of the engine 3 is transmitted to the first and second cutting blades 11 and 12 and the rear wheel 7.

  As shown in FIGS. 4, 5, and 9, the transmission shaft 18 (corresponding to the traveling transmission shaft) can be rotated laterally (left and right) to the rear side of the transmission shaft 17 so as to be orthogonal (intersect) with the transmission shaft 17. Has been placed. A worm gear 19a is connected to the transmission shaft 17, a worm wheel 19b is connected to the transmission shaft 18, and the worm gear 19a is engaged with the worm wheel 19b. A worm gear mechanism 19 is constituted by the worm gear 19a and the worm wheel 19b.

  As shown in FIGS. 4, 5, and 9, the transmission shaft 20 is supported on the rear side of the transmission shaft 18 so as to be rotatable in a lateral direction (left-right direction) parallel to the transmission shaft 18. A low-speed gear 23 and a high-speed gear 24 are connected to the parts of the transmission shaft 18 on both outer sides of the worm wheel 19b of the worm gear mechanism 19, and the low-speed gear 25 and the high-speed gear 26 are supported on the transmission shaft 20 so as to be relatively rotatable. The low speed gears 23 and 25 are engaged, and the high speed gears 24 and 26 are engaged.

  As shown in FIGS. 5 and 9, a shift member 27 is supported on the transmission shaft 20 between the low speed and high speed gears 25 and 26 by a spline structure so as to be rotatable and slidable integrally with the transmission shaft 20. The member 27 is biased by a pair of springs 70 to a neutral position where the member 27 does not mesh with the low speed and high speed gears 25 and 26 (disengagement state of the traveling clutch 35). Accordingly, the low-speed and high-speed gears 25 and 26 and the shift member 27 constitute an occlusal travel clutch 35.

  As shown in FIGS. 1, 2, and 3, a cylindrical support portion 13 b is connected to the bracket 13 a of the support frame 13 in the horizontal direction (left and right direction), and the drive shaft 28 is rotatably supported by the support portion 13 b. The rear wheel 7 is connected to one end of the drive shaft 28. As shown in FIGS. 1, 2, 3, 5, and 9, the transmission shaft 20 protrudes to the right from the first support case 21, and a sprocket 20 a is connected to the protruding portion of the transmission shaft 20. A transmission chain 29 is wound around the sprocket 28 a and the sprocket 20 a of the transmission shaft 20.

  As shown in FIGS. 1, 2, and 3, the cover 30 is connected across the first support case 21 and the support bracket 13 a of the support frame 13, and the transmission shaft 20 and the sprocket 20 a of the drive shaft 28 are connected by the cover 30. 28a, the transmission chain 29 is covered. A support member 34 is supported around the horizontal axis P4 of the support bracket 13a of the support frame 13 so that the position of the support chain 34 can be changed up and down, and a tension ring 33 that maintains the tension of the transmission chain 29 is rotatably supported by the support member 34. Has been.

  5 and 9, the engine 3 is driven by the centrifugal clutch 16, the transmission shaft 17, the worm gear mechanism 19, the transmission shaft 18, the low-speed and high-speed gears 23 and 24, and the low-speed and high-speed gears 25 and 26. Has been communicated to. When the shift member 27 is operated to the neutral position (disengagement state of the traveling clutch 35), the power of the engine 3 is interrupted at the position of the shift member 27, and the walking mower (rear wheel 7) stops.

  As shown in FIGS. 5 and 9, when the shift member 27 is engaged with the low speed gear 25 (the transmission state of the traveling clutch 35), the power of the engine 3 is transferred from the low speed gears 23, 25 to the shift member 27, the transmission shaft 20, and the transmission. Via the chain 29 and the drive shaft 28, it is transmitted to the rear wheel 7 at a low speed, and the walking mower (rear wheel 7) moves forward.

  As shown in FIGS. 5 and 9, when the shift member 27 is engaged with the high speed gear 26 (the transmission state of the traveling clutch 35), the power of the engine 3 is transferred from the high speed gears 24, 26 to the shift member 27, the transmission shaft 20, and the transmission. Via the chain 29 and the drive shaft 28, it is transmitted to the rear wheel 7 at a high speed, and the walking mower (rear wheel 7) moves forward.

[4]
Next, the part to the 1st cutting blade 11 in a work transmission system is demonstrated.
As shown in FIGS. 5, 6, and 9, the first cutting blade drive shaft 31 is rotatably supported around the vertical axis P <b> 5 of the first support case 21 in parallel with the transmission shaft 17. The first cutting blade 11 is connected to the lower portion of the first cutting blade drive shaft 31, and the first cutting blade 11 is disposed inside the first cutting blade housing 1.

  As shown in FIGS. 4, 6, and 8, the first cutting blade 11 includes a horizontally long support portion 11 a connected to the lower portion of the first cutting blade drive shaft 31, and a vertical axis P <b> 3 at one end of the support portion 11 a. The upper and lower blades 11b are rotatably supported around the upper and lower blades 11b, and the upper and lower blades 11b are rotatably supported around the vertical axis P3 at the other end of the support portion 11a. ing.

  As shown in FIGS. 5, 6, and 9, a small-diameter transmission gear 36 (corresponding to a gear mechanism) that is a flat gear is fixed to the upper portion of the transmission shaft 17, and a large-diameter transmission gear 37 (gear mechanism) that is a flat gear. Is supported on the upper portion of the first cutting blade drive shaft 31 so as to be relatively rotatable, and the transmission gears 36 and 37 are engaged with each other. Thereby, in the transmission shaft 17, the transmission gear 36 is positioned at the upper vertical position, and the worm gear mechanism 19 is positioned at the lower vertical position of the transmission gear 36.

  As shown in FIGS. 5, 6, and 9, a shift member 38 is supported on the upper portion of the first cutting blade drive shaft 31 by a spline structure so as to be integrally rotatable and slidable with the first cutting blade drive shaft 31. And a spring 39 that urges the transmission gear 37 toward the occlusal side (upward) with the transmission gear 37, and a cutting blade clutch 40 is configured between the transmission gear 37 and the shift member 38.

As shown in FIGS. 5, 6, and 9, the power of the engine 3 is transmitted from the centrifugal clutch 16 to the transmission shaft 17 and the transmission gears 36 and 37.
Thus, when the shift member 38 is engaged with the transmission gear 37 (the transmission state of the cutting blade clutch 40), the power of the engine 3 is transmitted to the first cutting blade drive shaft 31 via the shift member 38, and the first cutting blade The blade 11 is rotationally driven around the vertical axis P5. As described in [5] described later, the power of the engine 3 is transmitted to the second cutting blade drive shaft 32, and the second cutting blade 12 is moved. It is rotationally driven around the vertical axis P6.
When the shift member 38 is moved away from the transmission gear 37 (the cutting blade clutch 40 is disconnected), the power of the engine 3 is blocked at the position of the shift member 38 and the first and second cutting blades 11 and 12 are stopped.

  As shown in FIGS. 3, 5, and 6, the operation shaft 43 in the lateral direction (front-rear direction) is rotatably supported by the first support case 21, and the arm 43 a of the operation shaft 43 is engaged with the shift member 38. An operation arm 43b made of a spring wire is connected to the portion of the operation shaft 43 that protrudes from the first support case 21 to the outside.

The state shown in FIG. 6 is a state in which the shift member 38 is engaged with the transmission gear 37 (the transmission state of the cutting blade clutch 40). In the state shown in FIG. 6, the operation shaft 43 is rotated by pushing down the operation arm 43 b of the operation shaft 43, and the shift member 38 is moved downward from the transmission gear 37 against the spring 39 by the arm 43 a of the operation shaft 43. (The cutting blade clutch 40 is closed).
Next, by engaging the engaging arm (not shown) of the first support case 21 with the operating arm 43b of the operating shaft 43 depressed, the cutting blade clutch 40 can be maintained in the disconnected state.

[5]
Next, the part to the 2nd cutting blade 12 in a work transmission system is demonstrated.
As shown in FIGS. 5, 6, and 9, the transmission gear 37 is rotatably supported by the first cutting blade drive shaft 31 so as to be positioned at the upper and lower positions above the transmission shaft 18. A bevel gear 41 (corresponding to a first bevel gear) is fixed to the first cutting blade drive shaft 31 so that the lower portion of the spring 39 is supported by the bevel gear 41 so as to be positioned at the vertical position on the side.

  As shown in FIGS. 5, 6, and 9, the transmission shaft 44 (corresponding to the cutting blade transmission shaft) rotates sideways (left and right) toward the left side of the upper portion of the first support case 21 toward the second cutting blade housing 22. A bevel gear 42 (corresponding to a second bevel gear) that is supported freely and fixed to the transmission shaft 44 is engaged with the bevel gear 41. As a result, the transmission shaft 44 and the bevel gear 42 are positioned at the upper and lower positions between the transmission gear 37 and the bevel gear 41, and the power of the first cutting blade drive shaft 31 is transmitted to the transmission shaft 44 via the bevel gears 41 and 42. Communicated.

  As shown in FIGS. 2, 3, and 6, the second support case 22 is connected to the upper portion of the second cutting blade housing 2, and the second cutting blade drive shaft 32 is around the vertical axis P <b> 6 of the second support case 22. Is supported rotatably. The second cutting blade 12 is connected to the lower portion of the second cutting blade drive shaft 32, and the second cutting blade 12 is disposed inside the second cutting blade housing 2.

  As shown in FIGS. 6 and 8, the second cutting blade 12 has a horizontally long support portion 12a connected to the lower portion of the second cutting blade drive shaft 32, and a vertical shaft core P7 around one end of the support portion 12a. The upper and lower blades 12b are rotatably supported on the upper and lower blades 12b, and the upper and lower blades 12b are rotatably supported around the vertical axis P7 at the other end of the support portion 12a. Yes.

  As shown in FIGS. 6 and 9, the bevel gear 51 provided with the long boss portion 51 a is in a lateral orientation (left-right direction) with the boss portion 51 a (rotating shaft core) of the bevel gear 51 facing the first cutting blade housing 1. The bevel gear 52 that is rotatably supported inside the second support case 22 and is fixed to the upper portion of the second cutting blade drive shaft 32 is engaged with the bevel gear 51 inside the second support case 22.

As shown in FIGS. 6 and 9, a boss 51 a of the bevel gear 51 is formed with a hexagonal section hole, and the transmission shaft 45 having a hexagonal section has a boss of the bevel gear 51 so as to rotate and slide integrally with the bevel gear 51. One end of the transmission shaft 45 is located inside the second support case 22 and the other end of the transmission shaft 45 is located outside the second support case 22. The transmission shaft 44 and the other end of the transmission shaft 45 are connected via two universal joints 46 (universal joints).
In this case, since the two universal joints 46 are directly connected to each other in series, the other universal joint 46 is connected to the appropriate phase in the rotation direction with respect to the one universal joint 46. Thereafter, it is not necessary to separate the two universal joints 46 from each other.

  As shown in FIGS. 3 and 6, a bellows-like cover 55 made of rubber is connected across the transmission shafts 44 and 45 so as to cover the two universal joints 46, so that the sheet metal has a U-shaped cross section. A bent tunnel-shaped cover 56 is connected to the second cutting blade housing 2, and the cover 55 covers the cover 55. A tunnel-like cover 57 obtained by bending a sheet metal into a U-shaped cross section is connected to the first cutting blade housing 1, and the transmission shaft 44 and the cover 56 are covered by the cover 57.

As shown in FIGS. 6 and 9, the two universal joints 46 are connected to each other so that the length required for the two universal joints 46 (the length of the cover 55) is short.
Thereby, since the space | interval of the universal joint 46 and the 1st support case 21 becomes a thing large, in the 1st support case 21, the space | interval of a pair of bearing which supports the transmission shaft 44 can be set large. The transmission shaft 44 can be stably supported.
Similarly, since the space between the universal joint 46 and the second support case 22 is large, the distance between the pair of bearings supporting the bevel gear 51 in the second support case 22 can be set large. The bevel gear 51 can be stably supported.

As shown in FIGS. 6 and 9, the universal joint 46 and the transmission shaft 44 are connected by a shear pin (not shown) as a torque limiter, and the universal joint 46 and the transmission shaft 45 are connected as a shear pin (not shown). Z).
Thereby, even if the shear pin is broken, the shear pin can be easily replaced by removing the covers 56 and 57 from the first and second cutting blade housings 1 and 2.

  6 and FIG. 9, the power of the first cutting blade drive shaft 31 is transmitted through the bevel gears 41 and 42, the transmission shaft 44, the universal joint 46, the transmission shaft 45, and the bevel gears 51 and 52. 2 is transmitted to the cutting blade drive shaft 32, and the second cutting blade 12 is rotationally driven around the vertical axis P6.

[6]
Next, a structure in which the posture of the second cutting blade housing 2 is vertically changed with respect to the first cutting blade housing 1 around the longitudinal axis P1 will be described.
As shown in FIG. 7, when mowing the road surface and the slope as an inclined surface facing downward from the road surface, the second cutting blade housing 2 is set obliquely downward with respect to the first cutting blade housing 1, and The cutting blade 11 cuts the road surface, and the second cutting blade 12 cuts the slope.

  As shown in FIGS. 1, 2, 13, 14, and 15, a bracket 47 is connected downward to the right steering handle 4, and an operating lever 48 is supported by a lateral pin 47a of the bracket 47 so as to be swingable back and forth. And a spring 49 for pressing the base of the operation lever 48 against the bracket 47. The hole of the operating lever 48 into which the pin 47a of the bracket 47 is inserted is set to be slightly larger, and the operating lever 48 can be swung back and forth around the pin 47a of the bracket 47, and at the same time the operating lever 48 is It can be operated slightly to the left and right against the spring 49.

  As shown in FIGS. 1, 2, 13, 14, and 15, a flat lever guide 50 is connected to the right steering handle 4, and an operation lever 48 is inserted into the opening 50e of the lever guide 50 to extend upward. Has been issued. A parallel position 50a, a first lowered position 50b, a second lowered position 50c, and a third lowered position 50d are provided in the opening 50e of the lever guide 50. The end of the outer 53 b of the wire 53 is connected to the front portion of the lever guide 50, and the inner 53 a of the wire 53 is connected to the operation lever 48.

  As shown in FIGS. 2, 3, 6, and 7, the arm 54 is supported by the support pin 22 a that is connected to the second support case 22 so as to be swingable up and down, and the stopper pin 22 b is the second pin. It is connected to the support case 22. A bracket 58 is connected to the first cutting blade housing 1, an outer 53 b of the wire 53 is connected to the bracket 58, and an inner 53 a of the wire 53 is connected to the arm 54.

[7]
Next, based on the structure described in the preceding item [6], an operation of changing the posture of the second cutting blade housing 2 up and down around the front and rear axis P1 with respect to the first cutting blade housing 1 will be described.
The state shown in FIGS. 6, 13, and 14 is a state in which the operating lever 48 is operated and held at the parallel position 50a of the lever guide 50, and the connection portion 53c of the inner 53a of the wire 53 with the arm 54 is shown in FIG. It is located in the position shown.

  In the state shown in FIG. 6, the arm 54 is in contact with the stopper pin 22 b of the second support case 22, so that the second cutting blade housing 2 cannot move downward due to its own weight (the connection portion of the wire 53 in the fixed state). 53c, the second support case 22 (support pin 22a) cannot move downward), and the second cutting blade housing 2 is held in a posture parallel to the first cutting blade housing 1. .

  As shown in FIGS. 7, 13, and 14, when the operation lever 48 is operated and held at the first lowered position 50 b (second lowered position 50 c) (third lowered position 50 d) of the lever guide 50, the connecting portion of the wire 53 53c moves a little downward from the position shown in FIG. 6 and is fixed. Along with this, the arm 54 swings counterclockwise in FIG. 7 and moves away from the stopper pin 22b of the second support case 22 slightly upward.

  As a result, as shown in FIG. 7, the second cutting blade housing 2 is in a state in which the posture can be changed slightly downward from the posture parallel to the first cutting blade housing 1, and the second cutting blade housing 2 is moved downward. When the posture is changed, the arm 54 swings around the support pin 22 a of the second support case 22 in the clockwise direction in FIG. 7, and the posture of the arm 54 hitting the stopper pin 22 b of the second support case 22 is changed. The lower cutting posture of the second blade housing 2 is obtained.

As described above, the second cutting blade housing 2 is in a state in which the posture can be freely changed up and down between the posture parallel to the first cutting blade housing 1 and the lower limit posture, and the second front wheel 6 is the slope. , The second cutting blade housing 2 changes its posture up and down along the slope.
By operating and holding the operation lever 48 at the first lowered position 50b, the second lowered position 50c, and the third lowered position 50d of the lever guide 50, the lower limit posture of the second cutting blade housing 2 is set in three stages up and down. The third lowering position 50d of the lever guide 50 corresponds to the lower limit posture of the second cutting blade housing 2 that is located at the lowest position.

[8]
Next, as described in [7], the state of the second support case 22 and the transmission shaft 45 when the second cutting blade housing 2 is vertically changed will be described.
As described in [7] above, when the posture of the second cutting blade housing 2 is changed up and down, as shown in FIGS. 6 and 7, the transmission shaft 45 changes up and down with the universal joint 46 as a bending point. On the other hand, the position of the second support case 22 is also changed to the left and right at the same time the posture is changed vertically.

In this case, as shown in the preceding item [5] and FIG. 6, a hexagonal section hole is formed in the boss 51 a of the bevel gear 51, and the transmission shaft 45 having a hexagonal section is integrally rotated and slid with the bevel gear 51. The bevel gear 51 is freely inserted into the boss portion 51a.
As a result, as shown in FIGS. 6 and 7, when the bevel gear 51 (second support case 22) slides with respect to the transmission shaft 45, the second support case 22 changes its posture up and down, and at the same time is positioned in the left and right. The change state is allowed, and the bevel gear 51 (second support case 22) slides to the left (outside) with respect to the transmission shaft 45 as the second cutting blade housing 2 changes its posture downward (bevel gear 51). (The transmission shaft 45 is pulled out from the second support case 22).

As shown in FIGS. 6 and 7, a disc-shaped stopper member 59 is connected to one end of the transmission shaft 45 located inside the second support case 22 by a bolt 60.
In this case, the state in which the operation lever 48 is operated to the third lowered position 50d is a state in which the lower limit posture of the second cutting blade housing 2 is located at the lowest position, and the second cutting blade housing 2 is moved downward to the lower limit posture. The length of the wire 53 (inner 53a) is set so that the bevel gear 51 does not hit the stopper member 59 even if it is changed.

  However, the wire 53 (inner 53a) may be extended due to long-term use or the like. Even when the wire 53 (inner 53a) is extended, the bevel gear 51 hits the stopper member 59, so that the second cutting blade housing is further increased. 2 cannot change its posture downward.

  As shown in FIGS. 6 and 7, a grease nipple 61 for filling grease is provided at the upper center of the second support case 22 (substantially above the second cutting blade drive shaft 32). Accordingly, the grease can be supplied from the grease nipple 61 to the inside of the second support case 22, and the bevel gears 51 and 52 located inside the second support case 22, between the bevel gear 51 and the transmission shaft 45 can be supplied. You can replenish the part with grease.

[9]
Next, the structure of the accelerator lever 64 that operates the accelerator of the engine 3 will be described.
As shown in FIGS. 1, 2, 10, 11, and 12, a pipe-like support portion 62 is connected laterally (laterally) to the lower surface of the front side of the grip portion 4 a of the left steering handle 4. A base portion 65 is formed by bending a plate material, the base portion 65 is supported so as to swing up and down around the horizontal axis P8 of the support portion 62, and a round bar-like accelerator lever 64 is connected to the base portion 65. 64 is located below the grip portion 4a of the left steering handle 4, and is supported so as to be swingable up and down around the horizontal axis P8 of the left steering handle 4 (support portion 62).

  As shown in FIGS. 10, 11, and 12, the right and left vertical wall portions 65a of the base portion 65 extend upward, and the upper wall portion 65b is formed over the upper portions of the right and left vertical wall portions 65a. Yes. The right steering handle 4 passes through the opening between the vertical wall 65a and the upper wall 65b of the base 65, and the upper wall 65b of the base 65 hits the upper surface of the left steering handle 4, whereby the accelerator lever 64 lower limit postures are set.

  As shown in FIGS. 10, 11, and 12, the bracket 4 b is connected to the left steering handle 4, and the outer 66 b of the wire 66 is connected to the bracket 4 b of the left steering handle 4. An inner 66a of the wire 66 is connected to an arm 64a that is laterally coupled to the accelerator lever 64 via a spring 68 for accommodation, and the inner 66a of the wire 66 is connected to an accelerator (not shown) of the engine 3. .

The accelerator of the engine 3 is urged so as to return to the idling position, and the inner 66a of the wire 66 is pulled toward the engine 3 side.
The state shown in FIG. 1 and FIG. 10 is a state where the accelerator of the engine 3 is located at the idling position and the accelerator lever 64 is located at the idling position that is the lower limit posture, and the accelerator lever 64 is located on the left steering handle 4. It is located on the lower side at a predetermined interval from the grip portion 4a.

[10]
Next, the structure of the travel clutch lever 63 that operates the travel clutch 35 will be described.
As shown in FIGS. 10, 11, and 12, a traveling clutch lever 63 is formed by bending a vertically long plate material into a curved shape, and the base 63a of the traveling clutch lever 63 is positioned outside the base 65 (accelerator lever 64). The left steering handle 4 is supported so as to swing up and down around the horizontal axis P8 of the support portion 62.

  As a result, as shown in FIGS. 10, 11, and 12, the traveling clutch lever 63 is positioned below the grip portion 4 a of the left steering handle 4. The lateral width of the travel clutch lever 63 is configured to be sufficiently larger than the lateral width of the accelerator lever 64, and the travel clutch lever 63 is configured to extend rearward longer than the accelerator lever 64.

As shown in FIGS. 10, 11, and 12, the outer 67 b of the wire 67 is coupled to the bracket 4 b of the left steering handle 4, and the inner portion of the wire 67 is connected to the connecting portion 63 b extending laterally from the traveling clutch lever 63. 67a is connected via a spring 68 for flexibility.
The travel clutch 35 (see FIGS. 5 and 9) is provided with a switching mechanism (not shown), and the inner 67a of the wire 67 is connected to the switching mechanism. As shown in FIGS. 5 and 9, the shift member 27 is biased to the neutral position (blocking position) by the pair of springs 70, whereby the inner 67 a of the wire 67 is pulled toward the switching mechanism. Yes.

  The switching mechanism includes a low-speed state in which the shift member 27 in the neutral position is operated to the occlusion side to the low-speed gear 25 by the pulling operation of the wire 67 (inner 67a), and the engagement of the shift member 27 in the neutral position to the high-speed gear 26. It is configured to be switchable to a high-speed state operated to the side, and an operator manually operates the switching mechanism in a low-speed and high-speed state in advance.

The state shown in FIG. 1 and FIG. 10 is a lower limit posture in which the shift member 27 is positioned in the neutral position (disengaged state of the traveling clutch 35) and the base 63a of the traveling clutch lever 63 hits the lower surface of the left steering handle 4. It is in a state of being located at a certain blocking position.
In this state, the traveling clutch lever 63 in the shut-off position is positioned below the accelerator lever 64 in the idling position at a predetermined interval, and between the travel clutch lever 63 in the shut-off position and the left steering handle 4. The accelerator lever 64 at the idling position is located.

[11]
Next, the operation of the travel clutch lever 63 and the accelerator lever 64 will be described (No. 1).
As shown in FIGS. 1 and 10, when the hand is released from the traveling clutch lever 63 and the accelerator lever 64, the traveling clutch lever 63 is located at the shut-off position and the accelerator lever 64 is located at the idling position ( (The closed state of the centrifugal clutch 16).

In the state shown in FIGS. 1 and 10, the left hand is placed on the grip 4 a of the left steering handle 4, and the left clutch is held by holding the travel clutch lever 63 with the finger of the left hand. To be operated.
In this case, the switching mechanism described in [10] is operated in advance to a low speed state or a high speed state, and the cutting clutch 40 (see FIGS. 6 and 9) is operated to the transmission state in advance.

As shown in FIGS. 10, 11, and 12, when the travel clutch lever 63 is operated upward to a position where it contacts the accelerator lever 64 in the idling position, the pulling operation of the inner 67 a of the wire 67 causes the shift member 27 to move to the low speed gear 25 ( It is operated to a position where it meshes with the high speed gear 26) (the transmission state of the traveling clutch 35).
In this case, since the accelerator lever 64 (accelerator of the engine 3) is in the idling position, the centrifugal clutch 16 is in the disconnected state, and the rear wheel 7, the first and second cutting blades 11 and 12 are stopped.

As shown in FIGS. 10, 11, and 12, when the traveling clutch lever 63 is operated upward by grasping the left hand from the above-described state, the traveling lever lever 63 hits the accelerator lever 64, so that the accelerator lever 64 is also in the idling position. (The accelerator of the engine 3 is operated to the high speed side), and accordingly, the rotational speed of the engine 3 increases from the idling state. As described above, the grip portion 4a of the left steering handle 4, the travel clutch lever 63, and the accelerator lever 64 can be gripped together.
In this case, since the shift member 27 is not operated beyond the position where it engages with the low speed gear 25 (high speed gear 26), the upward operation of the travel clutch lever 63 is allowed by the extension of the spring 68.

As described above, when the rotational speed of the engine 3 increases from the idling state, the centrifugal clutch 16 enters the transmission state, and the power of the engine 3 is transmitted to the rear wheel 7, the first and second cutting blades 11, 12. Thus, the walking type mower (rear wheel 7) moves forward, and the first and second cutting blades 11 and 12 are driven to rotate.
When the left hand is grasped and the travel clutch lever 63 and the accelerator lever 64 are manipulated to a position where they are in contact with the grip 4a of the left steering handle 4, the accelerator of the engine 3 is manipulated to the highest speed position.

[12]
Next, the operation of the travel clutch lever 63 and the accelerator lever 64 will be described (No. 2).
As shown in FIGS. 1 and 10, the traveling clutch lever 63 is located at the shut-off position and the accelerator lever 64 is located at the idling position when the hand is released from the traveling clutch lever 63 and the accelerator lever 64. In this state, there is a space between the traveling clutch lever 63 and the accelerator lever 64.
In the state shown in FIG. 10, the cutting clutch 40 (see FIGS. 6 and 9) is operated in advance, the left hand is placed on the grip 4 a of the left steering handle 4, and the left hand finger is moved to the travel clutch. By placing the lever 63 between the lever 63 and the accelerator lever 64 and grasping the left hand, the accelerator lever 64 is operated upward.

As a result, in a state where the traveling clutch lever 64 remains in the disengaged position (disengaged state of the traveling clutch 35), the accelerator lever 64 is operated to the high speed side (the accelerator of the engine 3 is the high speed side), and the centrifugal clutch 16 is transmitted. Therefore, the first and second cutting blades 11 and 12 can be rotationally driven in a state where the walking mower (rear wheel 7) is stopped.
As described above, the state in which the accelerator lever 64 is operated to the high speed side (the accelerator of the engine 3 is the high speed side) with the traveling clutch lever 64 left in the disengaged position (disengaged state of the traveling clutch 35) is as follows. It is a state.

When mowing grass stays inside the first and second cutting blade housings 1 and 2 during the mowing operation, the hands are released from the traveling clutch lever 63 and the accelerator lever 64, and the walking type mower (rear wheel 7), first And the second cutting blades 11 and 12 are stopped, the right and left steering handles 4 are pushed down to bring the first and second cutting blade housings 1 and 2 into the forwardly raised state, and the first and second cutting blades 11 and 12 are moved. Position it above the ground.
Next, with the traveling clutch lever 64 left in the disengaged position (disengaged state of the traveling clutch 35), the accelerator lever 64 is operated on the high speed side (the accelerator of the engine 3 is on the high speed side), thereby With the rear wheel 7) stopped, the first and second cutting blades 11 and 12 located above the ground are idled and stay in the first and second cutting blade housings 1 and 2. The cut grass is forcibly released by the first and second cutting blades 11 and 12.

  In addition to the state described above, the rear wheel 7 can be freely rotated by leaving the traveling clutch lever 64 in the disengaged position (disengaged state of the traveling clutch 35). In this state, the accelerator lever 64 Is operated on the high speed side (the accelerator of the engine 3 is on the high speed side), so that the operator holds the right and left steering handles 4 and pushes the walking mower, The cutting operation can be performed by rotating 12.

Next, the reaping clutch 40 (see FIGS. 6 and 9) is operated in the disconnected state, and as described in [11] above, the grip portion 4a of the left steering handle 4, the traveling clutch lever 63, and the accelerator lever If both are held together, the walking wheel mower can be advanced by rotating the rear wheel 7 while the first and second cutting blades 11 and 12 are stopped.
The state as described above is suitable for a case where the vehicle moves on the road without performing a cutting operation, and the switching mechanism may be operated in a high speed state.

[Another Embodiment of the Invention]
In the above-mentioned [Mode for Carrying Out the Invention], the following (1) to (6) may be adopted.
(1) The 2nd cutting blade housing 2 is abolished and it is comprised in the walk type grass mower provided with one cutting blade housing and a cutting blade.
(2) In place of the centrifugal clutch 16, a friction clutch that is manually operated to be in a transmission state and a cutoff state is provided.
(3) In the gear mechanism, the gear mechanism is constituted by three or more transmission gears instead of the two transmission gears 36 and 37.
(4) The power of the engine 3 is transmitted not only to the rear wheel 7 but also to the first front wheel 5 (or the first and second front wheels 5 and 6).
(5) In the traveling clutch 35, the high speed gears 24 and 26 are abolished, and the power of the engine 3 is transmitted only by the low speed gears 23 and 25. Alternatively, the low speed gears 23 and 25 are eliminated, and the power of the engine 3 is transmitted only by the high speed gears 24 and 26.
(6) The worm gear mechanism 19 is not provided at the lower vertical position of the gear mechanism, but the gear mechanism is provided at the lower vertical position of the worm gear mechanism 19 by reversing the upper and lower sides. In this configuration, the vertical relationship between the bevel gear 41 and the transmission gear 37 (the cutting blade clutch 40) is reversed, the bevel gear 41 is positioned on the upper side, and the transmission gear 37 (the cutting blade clutch 40) is positioned on the lower side. It will be.

  INDUSTRIAL APPLICABILITY The present invention can be applied to a walking type mower, and a cutting blade is configured by upper and lower blades supported so as to be freely rotatable around a vertical axis at one and the other end of a support portion. The present invention can be applied not only to a walking type mower but also to a walking type mower having a horizontally long blade as a cutting blade and a cutting drive shaft connected to the central portion of the blade.

DESCRIPTION OF SYMBOLS 1 Cutting blade housing 2 Another cutting blade housing 3 Engine 3a, 17 Output shaft 5, 6, 7 Traveling wheel 11 Cutting blade 12 Another cutting blade 18 Traveling transmission shaft 19 Worm gear mechanism 31 Cutting blade drive shaft 36, 37 Flat Gear, gear mechanism 40 Cutting blade clutch 41 First bevel gear 42 Second bevel gear 44 Cutting blade transmission shaft P5 Vertical axis

Claims (4)

A cutting blade that is driven to rotate around a vertical axis, a cutting blade housing that houses the cutting blade, another cutting blade that is located next to the cutting blade housing, and an upper portion of the cutting blade housing. An engine and traveling wheels,
An output shaft that transmits power of the engine and that extends downward, and a cutting blade drive shaft that is connected to the cutting blade and extends upward are arranged in parallel,
A gear mechanism having a flat gear is provided across the output shaft and the cutting blade drive shaft, and the power of the output shaft is transmitted to the cutting blade drive shaft via the gear mechanism,
A cutting blade transmission shaft that transmits the power of the cutting blade drive shaft to the other cutting blade is disposed sideways in a state of being positioned on one side with respect to the cutting blade drive shaft in the left-right direction of the machine body,
A traveling transmission shaft that transmits power to the wheels is disposed laterally so as to intersect the output shaft in a state where the traveling transmission shaft is located on the opposite side of the cutting blade drive shaft with respect to the cutting blade drive shaft in the horizontal direction of the machine body. A walking-type grass mower having a worm gear mechanism across the output shaft and the travel transmission shaft and transmitting the power of the output shaft to the travel transmission shaft via the worm gear mechanism.   The walking type mower according to claim 1, wherein the output shaft includes the gear mechanism and the worm gear mechanism so that the worm gear mechanism is positioned at an upper and lower position below the gear mechanism. A cutting blade that is rotationally driven around a vertical axis, a cutting blade housing that houses the cutting blade, an engine provided on an upper portion of the cutting blade housing, and a traveling wheel.
An output shaft that transmits power of the engine and that extends downward, and a cutting blade drive shaft that is connected to the cutting blade and extends upward are arranged in parallel,
A gear mechanism having a flat gear is provided across the output shaft and the cutting blade drive shaft, and the power of the output shaft is transmitted to the cutting blade drive shaft via the gear mechanism,
A travel transmission shaft that transmits power to the wheels is disposed laterally so as to intersect the output shaft, and a worm gear mechanism is provided across the output shaft and the travel transmission shaft, and the power of the output shaft is Transmitted to the travel transmission shaft through a worm gear mechanism,
The output shaft is provided with the gear mechanism and the worm gear mechanism so that the worm gear mechanism is positioned at a vertical position below the gear mechanism,
Next to the cutting blade housing, another cutting blade and another cutting blade housing that houses the another cutting blade,
The cutting blade drive shaft is provided with a first bevel gear at a lower vertical position on the lower side of the traveling transmission shaft, and a cutting blade transmission shaft for transmitting power to the other cutting blade is provided with the gear mechanism and the first Place it sideways so that it is positioned up and down with the bevel gear,
Said second bevel gear having a cutting blade transmission shaft is occlusal to the first bevel gear, you are transmitting the power of the cutting blade drive shaft to the cutting blade transmission shaft through the first and second bevel gear step Row type mower.   The walking type mower according to claim 3, further comprising a cutting blade clutch capable of transmitting and closing the power of the gear mechanism to the cutting blade drive shaft at a connecting portion between the gear mechanism and the cutting blade drive shaft.

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