JP6541567B2 - Walking type work machine - Google Patents

Description

  The present invention relates to a walking type work machine, and more specifically, a traveling machine body having a pair of traveling devices on the left and right, a support frame supported by the traveling machine body so as to be vertically pivotable, and the support frame supported by the support frame A work unit to ground to the front, an engine supported by the support frame, and an engine that outputs a driving force to the work unit, supported by the support frame, and the output of the engine input to the hydrostatic stepless transmission unit The present invention also relates to a walking-type work machine provided with a traveling mission that distributes and transmits the output of the hydrostatic stepless transmission unit to the traveling devices on the left and right, and an elevation drive mechanism that swings the support frame.

  In the walking type work machine described above, by vertically swinging the support frame by the lifting and lowering drive mechanism, the working unit swings up and down relative to the traveling machine body, and the ground height of the working unit can be adjusted. Then, when the ground height of the working unit is adjusted, the engine and the traveling mission swing up and down together with the working unit, so the engine transmission is also transmitted to the traveling mission to the working transmission system that transmits the output of the engine to the working unit. The traveling transmission system does not need to be provided with a special flexible structure that enables the working unit to move up and down with respect to the traveling machine body.

  As this type of walking type work machine, for example, there is a walking type snow removal machine shown in Patent Document 1. In the walking type snow removal machine shown in Patent Document 1, the lifting and lowering cylinder causes the machine to swing up and down with respect to the crawler traveling device. A snow removal unit is connected to the front of the machine. An engine that transmits driving power to the snow removal unit is installed in the machine. The machine is provided with an HST transmission that receives the output of the engine and transmits the output to the crawler traveling device.

Japanese Patent Laid-Open No. 2000-64241

  In the above-described walking type work machine, the hydrostatic stepless transmission unit is equipped with a working oil tank communicated via an oil supply passage, so that the working oil tank replenishes the working oil to the hydrostatic stepless transmission unit. Is possible. If the working oil tank is rocked together with the hydrostatic stepless transmission part by adjusting the ground height of the working part, if the working posture of the working part is adjusted, the hydraulic oil tank will tilt and the working oil will shake, and the oil amount It is difficult to judge

  According to the present invention, it is possible to supply the hydraulic oil from the hydraulic oil tank to the hydrostatic continuously variable transmission unit, and to easily determine the oil amount of the hydraulic oil tank with high accuracy regardless of the adjustment of the ground height of the working unit. Provide mold work machines.

The walking type work machine according to the present invention is
A traveling body having a pair of left and right traveling devices, a steering handle supported so as not to be able to swing by the traveling body, a support frame supported so as to be vertically swingable by the traveling body, and a support frame A working unit that performs ground work in front of the traveling body, an engine that is supported by the support frame and that outputs driving force to the working unit, is supported by the support frame, and the output of the engine is hydrostatic stepless transmission Supported by the traveling handle which inputs to the control unit and distributes and transmits the output of the hydrostatic stepless transmission unit to the left and right traveling devices, an elevation driving mechanism for swinging the support frame, and the steering handle , a work dynamic fluid tank you storing hydraulic oil in the hydrostatic continuously variable transmission unit, and the oil supply passage having a flexible with communicating with said hydraulic fluid tank and the hydrostatic stepless speed change section, with a By integrally swing with respect to the engine and the working unit and the travel transmission is the traveling machine body together with the supporting frame, wherein the working unit is vertically movable upward and downward configuration with respect to the traveling machine body.
Further, in the present invention, it is preferable that the hydraulic oil tank is configured to allow the internal oil to be viewed.
Furthermore, in the present invention, the traveling transmission is provided with a pair of left and right output shafts extending in the left and right of the machine body and supporting the traveling device, and the supporting frame integrally swings with the traveling mission with the output shaft as an axis. It is preferable to move.

  According to this configuration, the support frame swings up and down with respect to the traveling machine even if the support frame is operated to move up and down by the elevating drive mechanism to adjust the work ground height, so It does not change. Even if the distance between the hydrostatic stepless transmission unit and the hydraulic oil tank changes due to the vertical rocking of the support frame, this change is absorbed by the deflection of the oil supply passage, so the height of the working part is adjusted. Even if the hydraulic oil tank does not tilt. By looking at the interior of the hydraulic oil tank by means of fluoroscopy, it is possible to see the inside of the hydraulic oil tank without vibrating it, since it is not necessary to open the lid of the hydraulic oil tank.

  Therefore, even if the height of the working part is adjusted, the hydraulic oil does not swing and the hydraulic oil does not shake, and there is no need to open the hydraulic oil tank lid and the hydraulic oil tank does not vibrate. The oil amount can be accurately determined regardless of the height adjustment of the working unit.

Further , according to this configuration, the operating handle can be supported at a position where the hydraulic oil tank can be easily viewed with a simple support structure using the operating handle for the hydraulic oil tank.

It is a side view showing the whole of a walk type snowblower. It is a top view which shows the whole of a walk type snowblower. It is a rear elevation showing a lift drive mechanism and a battery. It is a diagram showing a power transmission structure. It is a top view which shows a body frame and a support frame. It is a side view showing a rise-and-fall drive mechanism. It is a perspective view showing a body frame. It is a top view which shows a raising / lowering operation switch. It is a rear elevation showing the linkage mechanism in the disassembly state, and the operation part of a steering clutch and a steering brake. It is a side view showing a steering lever and an interlocking mechanism. It is a rear elevation showing steering lever and interlocking mechanism. It is a side view which shows the steering lever in the state which operated by weakening the steering brake, and the interlocking mechanism in the state. It is a side view which shows the steering lever in the state operated near the stroke end by the side of grip, and the interlocking mechanism in the state. It is explanatory drawing which shows the control system of steering operation and raising / lowering operation. It is an interlocking mechanism provided with another implementation structure, Comprising: It is a side view which shows the interlocking mechanism in the state which weakened and operated the steering brake. It is an interlocking mechanism provided with another implementation structure, Comprising: It is a side view which shows the interlocking mechanism in the state by which the steering lever was operated near the stroke end by the side of grip.

Hereinafter, embodiments of the present invention will be described based on the drawings.
FIG. 1 is a side view showing the whole of a walking snowplow according to an embodiment of the present invention. FIG. 2 is a plan view showing the entire walking snow remover according to the embodiment of the present invention. The direction of [F] shown in Figs. 1 and 2 is the "front side" of the traveling body, the direction of [B] is the rear side of the traveling body, and the direction of [L] is the left side of the traveling body, [R]. It is defined as the [right side] of the traveling aircraft.

  As shown in FIG. 1, the walking type snow removal machine is provided with a traveling machine body 3 in which a pair of left and right crawler traveling devices 2 are mounted on a machine body frame 1. The traveling body 3 is provided with a pair of left and right steering handles 4 provided at the rear, and is configured to be a walking type so as to perform traveling and steering operations of the traveling body 3 while walking behind the traveling body 3. A snow removal unit 10 is disposed in front of the traveling body 3. An engine 5 is disposed above the traveling airframe 3 behind the snow removal unit 10.

  In the walking type snow removal machine, the snow removal unit 10 can perform the snow removal operation by causing the traveling body 3 to travel. That is, the snow removal unit 10 includes an auger housing 11 and a blower case 12 connected to the rear of the auger housing 11. The auger 13 is rotatably supported by the auger housing 11. The blower 14 is mounted in the blower case 12 so as to be driven to rotate. A shooter 15 projects upward from the blower case 12. The auger 13 scrapes the snow, and the shooter 15 discharges the scraped snow from the outlet 15 a by the jet output of the blower 14.

The traveling machine 3 will be described.
As shown in FIGS. 1, 5 and 7, the vehicle body frame 1 includes a pair of left and right traveling vehicle body front-to-back track frame portions 20 and traveling vehicle body side-oriented connecting frame portions 21. The connecting frame portion 21 connects the rear portions of the left and right track frame portions 20. The longitudinal cross-sectional shape of the connection frame portion 21 is a groove shape opened in the front direction. The plan view shape of the airframe 1 is U-shaped opening in the forward direction. As shown in FIG. 5, the airframe frame 1 is internally provided with a vacant space in which a traveling mission 30 and a support frame 75 described later are placed.

  The left and right crawler traveling devices 2 are distributed to and supported by the left and right track frame portions 20, as shown in FIG. The left and right crawler traveling devices 2 are, as shown in FIGS. 1 and 5, a drive wheel 25 supported at the front end of the track frame portion 20 in a drivable manner and a track in a state positioned behind the drive wheel 25. A driven wheel body 26 rotatably supported by the frame portion 20 and a crawler belt 27 wound around the driving wheel body 25 and the driven wheel body 26 are provided. As shown in FIG. 1, the anti-slip member 28 is engaged with the crawler belt 27 between the drive wheel 25 and the driven wheel 26. The anti-slip member 28 is supported by the track frame portion 20.

  As shown in FIGS. 1 and 5, the pair of left and right steering handles 4 extend upward and rearward from the left and right end portions of the connection frame portion 21. Specifically, as shown in FIGS. 5 and 7, handle support frame portions 22 are provided at left and right end portions of the connection frame portion 21. The left and right handle support frame portions 22 project upward from the connection frame portion 21. The base 4 a of the steering handle 4 is supported by the handle support frame portion 22.

The left and right handle support frame portions 22 are configured by plate-like members. The plate-like member is attached to the connection frame portion 21 in an attachment posture in which the plate thickness direction is the traveling machine body lateral width direction. The bases 4 a of the left and right control handles 4 are supported by the side of the handle support frame portion 22 on the outer side of the vehicle body. The left and right control handles 4 are formed by round pipe members.
The base 4a of the left and right control handles 4 is subjected to a pressing deformation process so that a part of the outer peripheral surface becomes a flat surface. The base 4 a is connected to the handle support frame 22 with the flat surface being along the side surface of the handle support frame 22. In the present embodiment, the base 4a and the handle support frame portion 22 are connected by a connection bolt. The connection means between the base 4a and the handle support frame portion 22 is not limited to the connection bolt, and welding may be employed.

  A grip 4 b is provided at the extension end of the left and right control handles 4. The grips 4 b of the left and right control handles 4 extend in the front-rear direction of the traveling vehicle 3. As shown in FIG. 1, portions between the grips 4 b and the base 4 a of the left and right control handles 4 are connected by a pair of reinforcing rods 6, 7. The pair of reinforcing rods 6 and 7 are arranged at intervals in the vertical direction (longitudinal direction) of the steering handle 4. The left and right steering handles 4 are reinforced by supporting each other by the connection by the reinforcing rods 6 and 7. The control panel 8 is supported by the upper reinforcing rod 6.

  The left and right crawler traveling devices 2 and the snow removing unit 10 are driven by the driving force transmitted from the engine 5 based on the power transmission structure shown in FIG. 4.

That is, the output shaft 5a is protruded from the engine 5 in a forward direction. A travel clutch 31 is disposed across the output shaft 5 a and the input shaft 30 a of the travel mission 30. In the present embodiment, the traveling clutch 31 is configured by a belt tension clutch. The traveling clutch 31 is not limited to the belt tension clutch, and various types of clutches such as a multi-plate friction clutch may be adopted. Drive wheels 25 of the left and right crawler traveling devices 2 are supported by the left and right output shafts 30L, 30R of the traveling mission 30 so as to be relatively non-rotatable.
The traveling transmission 30 is provided with a hydrostatic continuously variable transmission unit 32 (hereinafter, abbreviated as HST 32). The HST 32 changes the driving force of the input shaft 30a by a variable displacement axial plunger pump (not shown) and an axial plunger motor (not shown), and changes the driving force after shifting to the left and right output shafts 30L, 30R. To communicate.

  By switching the traveling clutch 31 to the on state and shifting the HST 32 to the transmission state, the driving force from the engine 5 is transmitted to the left and right driving wheel bodies 25 and the left and right crawler traveling devices 2 are driven. The traveling body 3 can be traveled. By shifting the HST 32, the left and right crawler traveling devices 2 are switched between forward and reverse driving and driven, and the forward driving speed and the reverse driving speed of the left and right crawler traveling devices 2 are continuously shifted and traveling The airframe 3 can be switched between forward and reverse, and the vehicle can travel with no speed change between forward and reverse.

  By switching the traveling clutch 31 to the off state or shifting the HST 32 to the neutral state, the transmission of the driving force to the left and right crawler traveling devices 2 is interrupted, and the traveling body 3 can be stopped.

  The operation portion (tension pulley) of the traveling clutch 31 and the traveling clutch lever 33 (see FIGS. 1 and 2) are linked. The traveling clutch lever 33 is supported by the left steering handle 4. Specifically, the traveling clutch lever 33 is positioned above the grip portion 4b of the left steering handle 4 so as to be able to vertically swing. By gripping the clutch lever 33, the traveling clutch 31 can be switched to the on state. The clutch lever 33 for traveling is configured in a deadman type. That is, by holding the clutch lever 33, the traveling clutch 31 can be maintained in the engaged state, and by releasing the holding operation of the clutch lever 33, the traveling clutch 31 is turned off. As shown in FIGS. 1 and 2, the shift lever 34 for shifting the HST 32 is provided on the operation panel 8.

  As shown in FIG. 4, a working clutch 35 is provided across the output shaft 5 a of the engine 5 and the input shaft 10 a of the snow removal unit 10. In the present embodiment, the working clutch 35 is constituted by a belt tension clutch. The working clutch 35 is not limited to the belt tension clutch, and various types of clutches such as a multi-plate friction clutch may be adopted.

  By switching the work clutch 35 to the on state, the driving force from the engine 5 is transmitted to the input shaft 30a, and the auger 13 and the blower 14 can be driven. By switching the work clutch 35 to the off state, the transmission of the driving force to the input shaft 30a is cut off, and the auger 13 and the blower 14 can be stopped.

  The operation part (tension pulley) of the work clutch 35 and the clutch lever 36 (refer to FIG. 2) for work are linked. The working clutch lever 36 is supported by the right steering handle 4. Specifically, the clutch lever 36 is positioned above the grip portion 4b of the right steering handle 4 so as to be able to vertically swing. By gripping the clutch lever 36, the work clutch 35 can be switched to the on state.

  As shown in FIG. 14, the traveling transmission 30 is provided with a pair of steering clutches 37L, 37R on the left and right and a pair of steering brakes 38L, 38R on the left and right. The left and right steering clutches 37L and 37R are provided with clutch wheel bodies 39L and 39R. The clutch ring bodies 39L and 39R are slidably and relatively non-rotatably fitted on the outer peripheral portions of the splines of the output shafts 30L and 30R. Claw clutch mechanisms 41L, 41R are provided across the clutch ring bodies 39L, 39R and the output gear 40. The output gear 40 is supported by the left and right output shafts 30L, 30R in a state in which the output gear 40 can be made relative to the left and right output shafts 30L, 30R. The output gear 40 is driven by the output of the HST 32. The shifters 42L and 42R are engaged with the clutch wheels 39L and 39R. The left and right shifters 42L and 42R are swingably supported by the transmission case 44 (see FIG. 9) via the rotation support shafts 43L and 43R. As shown in FIG. 9, on the outside of the transmission case 44, the operation arms 45L, 45R are supported by the left and right rotation support shafts 43L, 43R so as to be relatively non-rotatable.

  As the shifters 42L and 42R are rocked by the rocking operation of the operation arms 45L and 45R, the clutch wheels 39L and 39R are moved close to the output gear 40 or separated from the output gear 40. By operating the clutch wheels 39L and 39R close to the output gear 40, the claw clutch mechanisms 41L and 41R are operated to be engaged. By operating the clutch wheels 39L and 39R to separate from the output gear 40, the claw clutch mechanisms 41L and 41R are turned off.

  The left and right steering clutches 37L and 37R are turned on by operating the claw clutch mechanisms 41L and 41R in the on state, and are turned off by operating the claw clutch mechanisms 41L and 41R in the off state. Become. The left and right steering clutches 37L and 37R are interlocked to interlock the output gear 40 and the output shafts 30L and 30R, and transmit the output of the HST 32 to the drive wheel 25. The left and right steering clutches 37L and 37R release the interlocking connection between the output gear 40 and the output shafts 30L and 30R by the claw clutch mechanisms 41L and 41R being turned off, and the HST 32 starts the crawler traveling device 2 Cut off the power transmission to.

  Left and right steering brake 38L. The 38R is constituted by a multi-plate friction clutch. In the operating range where the steering clutches 37L and 37R are switched to the off state, the clutch wheels 39L and 39R are engaged by the rocking operation of the shifters 42L and 42R by the rocking operation of the operating arms 45L and 45R. The steering spring 38 is operated against the steering brakes 38L and 38R or is operated away from the steering brakes 38L and 38R.

  The left and right steering brakes 38L and 38R are pressed by the operating portions 39a and 39b of the clutch wheels 39L and 39R, which are moved close to each other, and become in the entering state, and the operating portions are released by the clutch wheels 39L and 39R. When the pressure by 39a and 39b is released, it will be in a cutting state. When the left and right steering brakes 38L and 38R are in the on state, they apply friction braking force to the output shafts 30L and 30R and apply a brake to the crawler travel device 2. The left and right steering brakes 38L and 38R strengthen the brakes applied to the crawler travel device 2 as the pressing force of the clutch wheel 39L39R is intensified. When the left and right steering brakes 38L and 38R are turned off, the application of the friction braking force to the output shafts 30L and 30R is released, and the brake applied to the crawler travel device 2 is released.

  As shown in FIGS. 9 and 14, one actuator 49 is linked to the left and right operation arms 45L and 45R via a linking mechanism 50. The left and right steering clutches 37L and 37R and the left and right steering brakes 38L and 38R can be operated by one actuator 49. In the present embodiment, an electric motor is employed as the actuator 49. The actuator 49 is not limited to the electric motor, and various power sources such as a cylinder may be employed. In the following, the actuator 49 will be described as being referred to as an electric motor 49.

  The linkage mechanism 50 includes a seesaw member 51, as shown in FIG. The seesaw member 51 is supported by the transmission case 44 via the support shaft 52. The seesaw member 51 can be rocked with the axis of the support shaft 52 as the rocking axis. The left and right end portions of the seesaw member 51 are connected to the left and right operation arms 45L, 45R by a pair of left and right interlocking links 53L, 53R. Ends 54L, 54R on the seesaw member side of the left and right interlocking links 53L, 53R are slidably engaged with long hole type connection holes 55L, 55R of the seesaw member 51.

  The seesaw member 51 and the electric motor 49 are interlocked and connected via a sector gear 56, a small diameter gear 57, a large diameter gear 58 and a worm gear 59. The sector gear 56 is provided with a connecting arm 56a. By mounting the support shaft 52 and the connection pin 56b over the connection arm portion 56a and the seesaw member 51, the sector gear 56 and the seesaw member 51 are connected so as not to be relatively rotatable. The sector gear 56 and the small diameter gear 57 mesh with each other. The small diameter gear 57 and the large diameter gear 58 are interlockingly connected via the rotation support shaft 60. The large diameter gear 58 and the worm gear 59 mesh with each other. The worm gear 59 is attached to the output shaft 49 a of the electric motor 49 so as not to be relatively rotatable.

  When the electric motor 49 is operated in the neutral state, the seesaw member 51 is in the neutral position [N]. In this case, the end portions 54L, 54R of the left and right interlocking links 53L, 53R are positioned at the arm side end portions of the connection holes 55L, 55R, and the left and right operation arms 45L, 45R are operated by the return spring 47 to the clutched position. There is. That is, the left and right steering clutches 37L and 37R are in the engaged state.

  When the electric motor 49 is operated from the neutral state to the left turning side, the seesaw member 51 is swung from the neutral position [N] in the left turning direction [LS], and the left interlocking link 53L is pulled by the seesaw member 51 As a result, the left operating arm 45L is swung from the clutched position toward the braked position, and the left steering clutch 37L is switched to the disengaged state. After the left steering clutch 37L is turned off, when the seesaw member 51 is further rocked in the left turning direction [LS], the left operating arm 45L is operated to the brake position, and the left steering brake 38 L will be in the state. The larger the swing stroke of the seesaw member 51 in the left turning direction [LS], the stronger the pressing force of the clutch wheel 39L on the left steering brake 38L, and the stronger the braking force of the left steering brake 38L. . Thus, when the left steering clutch 37L is in the disengaged state and the left steering brake 38L is in the engaged state, the right connecting hole 55R moves toward the right operating arm 45R, and the right The operating arm 45R is maintained in the clutch engaged position by the return spring 47, the right steering clutch 37R is maintained in the engaged state, and the right steering brake 38R is maintained in the disengaged state.

  When the electric motor 49 is operated from the neutral state to the right turning side, the seesaw member 51 is swung from the neutral position [N] in the right turning direction [RS], and the right interlocking link 53R is moved by the seesaw member 51. When the pulling operation is performed, the right operating arm 45R is swung from the clutched position toward the braked position, and the right steering clutch 37R is switched to the disengaged state. After the right steering clutch 37R is turned off, when the seesaw member 51 is further rocked in the right turning direction [RS], the right operating arm 45R is operated to the brake position, and the right steering The brake 38R is in the on state. As the swing stroke of the seesaw member 51 in the right turning direction [RS] becomes larger, the pressing force of the clutch wheel 39R against the right steering brake 38R becomes stronger, and the braking force of the right steering brake 38R becomes stronger Become. Thus, when the right steering clutch 37R is turned off and the right steering brake 38R is turned on, the left connecting hole 55L moves toward the left operating arm 45R and the left The operating arm 45L is maintained in the clutch engaged position by the return spring 47, the left steering clutch 37L is maintained in the engaged state, and the left steering brake 38L is maintained in the disengaged state.

  As shown in FIGS. 1 and 2, a pair of left and right steering levers 61 L and 61 R are distributed and supported by the left and right steering handle 4. Specifically, as shown in FIG. 10, a pair of left and right brackets 62 are provided so as to project downward from a portion on the front side of the grip portion 4b of the steering handle 4. The bracket 62 and the base of the steering levers 61L and 61R are connected via a support shaft 63. The steering levers 61L and 61R are raised and rocked with the axis of the support shaft 63 as the rocking axis X by gripping operation. The steering levers 61L and 61R are lowered and rocked by the operation force of the return spring 64 by releasing the grip operation. The return spring 64 is connected to an interlocking member 69 described later.

  As shown in FIGS. 10 and 11, the left operation position detection sensor 65L is interlockingly connected to the left steering lever 61L via the interlocking mechanism 66. The right operation position detection sensor 65R is interlockingly connected to the right steering lever 61L via the interlocking mechanism 66. The interlocking mechanism 66 of the left steering lever 61L and the interlocking mechanism 66 of the right steering lever 61R operate the operation position detection sensors 65L, 65R interlocked with the swing of the reference stroke [A] of the steering levers 61L, 61R. The steering levers 61L and 61R and the operation position detection sensors 65L and 65R are interlocked and linked in such a state that the amount of change becomes larger as the operation position of the steering levers 61L and 61R approaches the stroke end on the grip side.

  Specifically, the operation position detection sensors 65 </ b> L and 65 </ b> R are supported by the steering handle 4 via the bracket 67. The operation position detection sensors 65L and 65R are configured by rotary potentiometers.

  An interlocking mechanism 66 of the left steering lever 61L and the right steering lever 61R includes a swing arm 68 and an interlocking member 69. The swing arm 68 is extended so as not to be relatively rotatable from the rotation operation parts 70L, 70R of the operation position detection sensors 65L, 65R. The swinging arm 68 is swingable so that the axis of rotation of the rotation operation units 70L and 70R is the swinging axis Y, and the swinging operation is performed to operate the operation position detection sensors 65L and 65R.

  The interlocking member 69 is extended in the lateral inward direction of the vehicle from a portion of the base of the steering levers 61L, 61R which is separated from the swing axis X. The interlocking member 69 pivots integrally with the steering levers 61L and 61R with the pivot axis X as the pivot axis. The extension end side 69a of the interlocking member 69 is engaged with the long hole-shaped connecting hole 68a of the swing arm 68, and the link member 69 can slide in the swing arm longitudinal direction with respect to the swing arm 68 It is engaged with the swinging arm 68 in a state where the swinging operation of the swinging arm 68 is possible. The rocking axis Y of the rocking arm 68 and the rocking axis X of the steering levers 61L and 61R are misaligned and are parallel or substantially parallel.

  When the steering levers 61L and 61R are gripped, the interlocking member 69 pushes the swing arm 68 by the extension end side portion 69a to swing and the swing arm 68 rotates the operation position detection sensors 65L and 65R. Rotate the units 70L and 70R. As the gripping operation of the steering levers 61L and 61R proceeds, the extending end side portion 69a of the interlocking member 69 slides toward the free end of the oscillating arm 68, and the oscillating arm receives the oscillating operation by the interlocking member 69. Position 68 changes to the free end. By operating the reference stroke [A] with the steering levers 61L and 61R directed toward the stroke end on the grip side, the swing arm 68 swings by a swing angle [B] by the operation of the interlocking member 69. The swing angle [B] of the swing arm 68 increases as the steering levers 61L and 61R approach the grip stroke end. As the steering levers 61L, 61R approach the grip stroke end, the operation position detection sensors 65L, 65R respond more sensitively to the movement of the steering levers 61L, 61R.

  That is, the operation position of the left steering lever 61L is detected by the left operation position detection sensor 65L. The operating position of the right steering lever 61R is detected by the right operating position detection sensor 65R. In the left and right operation position detection sensors 65L and 65R, when the steering levers 61L and 61R are gripped and operated, the detection operation position is shifted to the stroke end on the grip side than the actual operation position. In the state, as the steering levers 61L and 61R approach the stroke end on the grip side, the positional deviation between the detection operation position and the actual operation position is detected in a state of becoming larger.

  As shown in FIG. 14, left and right operation position detection sensors 65 L, 65 R and an electric motor 49 are linked to the control device 71. The control device 71 is configured using a microcomputer, and includes a control unit 72 for steering (hereinafter referred to as a steering control unit 72).

  When the left and right steering levers 61L and 61R are not operated, the steering control unit 72 operates the seesaw member 51 to the neutral position [N] based on the detection information by the left and right operation position detection sensors 65L and 65R. To control the electric motor 49.

  When the left steering lever 61L is gripped, the steering control unit 72 rotates the seesaw member 51 from the neutral position [N] to the left turning direction [LS] based on the detection information by the left operation position detection sensor 65L. The electric motor 49 is controlled to cause the left steering brake 38L to have a braking force corresponding to the detection operation position detected by the left operation position detection sensor 65L.

  When the right steering lever 61R is gripped, the steering control unit 72 turns the seesaw member 51 from the neutral position [N] to the right turning direction [RS] based on the detection information by the right operation position detection sensor 65R. The electric motor 49 is controlled to make the right steering brake 38R have a braking force corresponding to the detection operation position detected by the right operation position detection sensor 65R.

  By operating the left and right steering levers 61L and 61R, the left and right steering clutches 37L and 37R and the left and right steering brakes 38L and 38R can be operated, and steering operation of the traveling vehicle 3 can be performed.

  That is, if the left and right steering levers 61L and 61R are not gripped, the seesaw member 51 is neutral due to the control of the electric motor 49 by the steering control unit 72 based on the detection information of the left and right operation position detection sensors 65L and 65R. The left and right steering clutches 37L and 37R are operated to be engaged as the position [N] is operated, and the traveling body 3 travels straight.

  When the left steering lever 61L is gripped, the steering control unit 72 controls the electric motor 49 based on the detection information of the left operation position detection sensor 65L to turn the seesaw member 51 from the neutral position [N] to the left turning direction [ The left steering clutch 37L is turned off, or the left steering brake 38L is turned on, and the traveling body 3 turns to the left. When the left steering brake 38L is in the on state, the left steering brake 38L is applied to the left crawler traveling device 2 with a strong braking force as the grip operation stroke of the left steering lever 61L is increased. And the left turn radius of the traveling vehicle 3 is smaller.

  When the right steering lever 61R is gripped, the steering control member 72 controls the electric motor 49 based on the detection information of the right operation position detection sensor 65R to turn the seesaw member 51 from the neutral position [N] to the right turning direction The right steering clutch 37R is turned off by being swung by [RS], or the right steering brake 38R is turned on so that the traveling body 3 turns to the right. When the right steering brake 38R is in the on state, the right steering brake 38R is applied to the right crawler traveling device 2 with a strong braking force as the grip operation stroke of the right steering lever 61R is increased. And the right turn radius of the traveling vehicle 3 is smaller.

  As the steering levers 61L and 61R approach the grip stroke end, the operation position detection sensors 65L and 65R respond more sensitively to the movement of the steering levers 61L and 61R, so the steering brakes 38L and 38R are effective. In the weak stage, by slightly operating the steering levers 61L and 61R, the effects of the steering brakes 38L and 38R change only slightly, and it is easy to finely adjust the braking force. At the stage where the steering brakes 38L and 38R are strong, the steering brakes 38L and 38R are greatly changed by slightly operating the steering levers 61L and 61R, so that the steering brakes 38L and 38R have a strong braking force. Easy to operate quickly to the state.

  As shown in FIGS. 1, 2 and 5, the snow removal unit 10 is supported by the support frame 75 by the blower case 12 being connected to the front end of the support frame 75. The engine 5 is supported by the support frame 75 in a state of being mounted on the upper portion of the support frame 75.

  The traveling mission 30 is supported by the lower portion of the support frame 75. Specifically, as shown in FIG. 5, in the traveling transmission 30, a pair of left and right cylindrical members extending outward in the lateral direction of the vehicle body from both lateral sides of the transmission case 44 and having the output shafts 30L and 30R installed therein. The output case parts 44L and 44R of The left and right output case parts 44L, 44R are supported by the lateral side 75a of the support frame 75, and the rear of the transmission case 44 is supported by the rear 75b of the support frame 75.

  The support frame 75 is supported by the traveling machine body 3 so as to be able to swing up and down with the rotational axis of the drive wheel body 25 of the left and right crawler traveling devices 2 as the oscillation axis Z. Specifically, the support frame 75 is positioned between the left and right track frame portions 20, and the left output case portion 44L of the traveling mission 30 is supported by the left track frame portion 20 of the airframe frame 1 so as to be relatively rotatable. The right output case portion 44R of the traveling mission 30 is supported by the right track frame portion 20 of the airframe frame 1 so as to be relatively rotatable.

  The support frame 75 is provided with an operation arm 76 extending rearward from the rear of the support frame 75. A lift drive mechanism 77 is provided across the extension end of the operation arm 76 and the machine body frame 1. The elevating drive mechanism 77 swings and adjusts the support frame 75 vertically with respect to the machine body frame 1 by being driven, and fixes the support frame 75 at the adjusted swing position by being stopped.

  By operating the elevation drive mechanism 77, the snow removal unit 10 can be adjusted up and down relative to the traveling machine body 3, and the ground height of the snow removal unit 10 can be adjusted. In order to adjust the height of the snow removal unit 10 with respect to the ground, the support frame 75 swings up and down with the rotational axis of the drive wheel 25 of the left and right crawler traveling device 2 as the swing axis Z. 5 and the traveling transmission 30 integrally swing up and down with the axis of rotation of the left and right drive wheels 25 as the axis of oscillation Z, a work transmission system for transmitting the driving force from the engine 5 to the snow removal unit 10, It is not necessary to provide a special flexible structure for allowing the raising and lowering of the snow removal unit 10 in the traveling transmission system for transmitting the driving force from the engine 5 to the left and right crawler traveling devices 2. In addition, even if the ground height of the snow removal unit 10 is changed, the ground attitude of the traveling vehicle 3 does not change, and the ground attitude of the steering wheel 4 does not change.

The elevation drive mechanism 77 includes a rack gear 78, a pinion gear 79, and an electric motor 80, as shown in FIGS. The rack gear 78 and the pinion gear 79 mesh with each other. An intermediate gear 79a is supported by the rotation support shaft of the pinion gear 79 so as not to be relatively rotatable.
An output gear 80a meshed with the intermediate gear 79a is rotatably supported by the electric motor 80. The pinion gear 79 and the output gear 80a of the electric motor 80 are interlockingly connected via an intermediate gear 79a.

As shown in FIGS. 3 and 6, the rack gear 78 is supported by the traveling machine body 3 in a state of projecting upward from the machine body frame 1. Specifically, the lower end portion of the member 78a provided with the rack gear 78 is supported by the bracket 85 so as to be relatively rotatable via the support shaft 78b. The bracket 85 is supported by the connecting frame portion 21 of the machine body frame 1. The pinion gear 79, the intermediate gear 79 a and the electric motor 80 are supported by the support member 81. The support member 81 is relatively rotatably supported by the rear end portion 76 a of the operation arm 76 via the support shaft 81 a.
In this embodiment, the rack gear 78 is supported by the body frame 1 and the pinion gear 79 is supported by the support frame 75. However, the rack gear 78 is supported by the support frame 75, and the pinion gear 79 is mounted to the body frame 1. A supported configuration may be employed.

  A guide groove 82 is provided in a member 78 a provided with the rack gear 78. A guide pin 83 slidably supported in the guide groove 82 is supported by the support member 81. The guide pin 83 supports the detent member 86. The separation prevention member 86 prevents separation of the rack gear 78 and the pinion gear 79 by preventing separation of the member 78 a and the support member 81.

  The elevating drive mechanism 77 drives the pinion gear 79 by the driving force of the electric motor 80, raises and lowers the pinion gear 79 along the rack gear 78, and raises and lowers the rear end side of the operation arm 76 to move the support frame 75. Swing operation. The elevating drive mechanism 77 applies the elevating operation force to the support frame 75 in the vicinity of the rear portion of the crawler belt 27 and away from the swinging axis Z of the support frame 75 (the rotation axis of the drive wheel 25). Vertical adjustment of the snow removal unit 10 can be smoothly performed by the small electric motor 80.

  The elevation drive mechanism 77 is disposed at a position near the rear of the crawler belt 27 between the left and right crawler traveling devices 2. The elevating drive mechanism 77 applies the elevating operation force at a position separated from the rotational axis of the drive wheel 25 to the vicinity of the rear portion of the crawler belt 27. Even in the case, the supporting frame 75 can be smoothly swung up and down by the lifting and lowering drive mechanism 77.

  The elevation drive mechanism 77 is located rearward of the engine 5. Since the lift drive mechanism 77 swings the support frame 75 behind the portion where the load of the engine 5 is applied, the operating force of the lift drive mechanism 77 can be efficiently applied to the swing operation of the support frame 75.

  The elevation drive mechanism 77 is located rearward of the rear end 1 r of the machine frame 1. Specifically, in a state where the snow removal unit 10 has risen to the rising limit, as shown by a solid line in FIG. 6, the whole of the lifting drive mechanism 77 from the lower end to the upper end is positioned behind the rear end 1r. In the state where the snow removal unit 10 is lowered to the descent limit, the lower end side portion of the lifting and lowering drive mechanism 77 is positioned rearward of the rear end 1 r as shown by a two-dot chain line in FIG. The distance from the rotational axis of the drive wheel 25 to the elevation drive mechanism 77 can be longer than that of the elevation drive mechanism 77 positioned forward of the rear end 1r, and the operation force of the elevation drive mechanism 77 is supported by the support frame It is made to act efficiently on the swing operation of 75. It is more preferable that the entire lifting drive mechanism 77 be positioned rearward of the rear end 1 r regardless of the position of the lifting and lowering range from the lowering limit to the rising limit.

  As shown in FIGS. 1, 3 and 5, the lifting drive mechanism 77 and the battery 84 for power supply are aligned in the lateral width direction of the traveling vehicle body. It is possible to suppress the protrusion of the battery 84 to the rear of the lift drive mechanism 77. In addition, the battery 84 is less likely to be an obstacle in performing inspection and repair work of the lift drive mechanism 77 from the rear of the traveling machine body.

  As shown in FIGS. 2 and 8, the elevating operation switch 87 is supported by the right steering handle 4 in a state in which it is positioned on the inner side of the grip 4 b of the right steering handle 4 in the lateral direction of the machine. The raising and lowering operation switch 87 is located at a portion where the finger operating the hand supporting the grip 4b can be operated. Specifically, a boss 88 is provided on the front side of the grip 4 b of the steering handle 4. The boss portion 88 supports the working clutch lever 36 so that it can be pivoted up and down. A support member 89 extends rearward from the boss portion 88. A lift operation switch 87 is supported at the extension end of the support member 89. In the present embodiment, the elevating operation switch 87 is supported by the right steering handle 4, but may be supported by the left steering handle 4.

As shown in FIG. 14, the elevation operation switch 87 and the electric motor 80 are linked to the control device 71. The control device 71 is called a control unit 90 for raising and lowering (hereinafter referred to as a raising and lowering control unit 90).
).

  Elevation control unit 90, when the operation information is inputted from elevation operation switch 87, moves the pinion gear 79 to the operation position on the rising side and the lowering side corresponding to the operation information based on the inputted operation information and makes it stop by the electric motor Control 80

  By pressing the front end side portion of the lifting and lowering operation switch 87, the lifting and lowering control unit 90 controls the electric motor 80 to move downward and the snow removal unit 10 can be lowered. By pressing the rear end side portion of the lifting and lowering operation switch 87, the lifting and lowering control unit 90 controls the electric motor 80 to move upward, and the snow removal unit 10 can be lifted and operated. As long as the snow removal unit 10 does not reach the stroke end while the lifting operation switch 87 is pressed, the snow removal unit 10 continues to be raised and lowered.

  As shown in FIGS. 1 and 2, the headlight 92 is supported by the traveling body 3. Specifically, the headlight 92 is supported by the steering handle 4 via the upper reinforcing rod 6. The headlight 92 is supported in a state in which the mounting orientation can be adjusted up and down. The headlight 92 is misaligned with respect to the shooter 15 in the traveling vehicle body width direction. It is possible to work while illuminating the front of the snow removal unit 10 and the like by the headlights 92 and illuminating the shooter 15 in a state that is unlikely to be an obstacle to the illumination. Since the headlights 92 are supported by the traveling body 3 that supports the support frame 75 so as to be able to swing up and down, the attitude of the headlights 92 does not change even if the snow removal unit 10 is adjusted up and down. That is, even if the snow removal unit 10 is adjusted up and down, the illumination condition such as the illumination range of the headlight 92 does not change.

  As shown in FIG. 1, a hydraulic oil tank 93 is supported by the traveling machine body 3. Specifically, as shown in FIG. 3, the hydraulic oil tank 93 is supported by the steering handle 4 via the lower reinforcing rod 7. The hydraulic oil tank 93 and the HST 32 communicate with each other by an oil supply passage 94. The oil supply passage 94 is formed by a flexible hose and has flexibility. That is, the oil supply passage 94 absorbs the change in the positional relationship between the HST 32 and the hydraulic oil tank 93 accompanying the vertical adjustment of the snow removal unit 10 by bending.

  By storing the hydraulic oil in the hydraulic oil tank 93, the hydraulic oil is automatically replenished to the HST 32. The hydraulic oil tank 93 is made of a material capable of seeing through the hydraulic oil inside. The amount of oil inside can be viewed without opening the lid of the hydraulic oil tank 93. Since the hydraulic oil tank 93 is supported by the traveling machine body 3 that supports the support frame 75 so as to be able to swing up and down, the hydraulic oil tank 93 does not tilt even if the snow removal unit 10 is adjusted up and down.

[Another embodiment]
(1) FIG. 15 is a side view showing an interlocking mechanism 66 having another embodiment, in which the steering brakes 38L and 38R are weakly operated and operated. FIG. 16 is a side view showing an interlocking mechanism 66 provided with another embodiment, in which the steering levers 61L and 61R are operated near the stroke end on the grip side. As shown in FIGS. 15 and 16, in the interlocking mechanism 66 having another embodiment, the interlocking member 69 is constituted by a rocking link. That is, the end on the steering lever side of the interlocking member 69 and the part of the steering levers 61L and 61R that is out of the swinging axis X are relatively rotatably connected via the support shaft 69b. The interlocking member 69 swings relative to the steering levers 61L and 61R with the axis of the support shaft 69b parallel or substantially parallel to the swing axis X as the swing axis.

(2) In the embodiment described above, the support frame 75 is rocked with the axis of rotation of the drive wheel 25 as the pivot axis Z. However, the support frame 75 is limited to the axis of rotation of the drive wheel 25 Alternatively, the rotary shaft core of the driven wheel 26 may be configured as a rocking shaft core, or a shaft core set at any other location may be configured as a rocking shaft core.

(3) In the embodiment described above, the elevation drive mechanism 77 has the rack gear 78, the pinion gear 79, and the electric motor 80. However, the elevation drive mechanism 77 may be configured by a hydraulic cylinder, an electric cylinder, etc. .

(4) Although the example which supported the hydraulic oil tank 93 to the control handle 4 was shown in the Example mentioned above, you may support on various support members, such as a support | pillar provided in the traveling body 3, for example.

(5) In the above-mentioned embodiment, although the example provided with the crawler traveling device 2 was shown, it may replace with the crawler traveling device 2 and may be equipped with a wheel.

  The present invention is a walking type mower having a lawn mower instead of the snow removing unit 10 in addition to a walking type snow remover, and various walking types such as a walking type mower having a mowing device instead of the snow removing unit 10. Applicable to work machines.

Reference Signs List 2 traveling device 3 traveling vehicle 4 steering handle 5 engine 30 traveling transmission 32 hydrostatic stepless transmission unit 75 support frame 77 elevation drive mechanism

Claims (3)

A traveling airframe having a pair of left and right traveling devices ,
A steering wheel non-swingably supported by the traveling body;
A support frame supported by the traveling body so as to be vertically swingable ;
A working unit supported by the support frame and working on the ground in front of the traveling airframe ;
An engine supported by the support frame and outputting a driving force to the working unit ;
A traveling mission supported by the support frame to input an output of the engine to a hydrostatic stepless transmission unit and distribute and transmit an output of the hydrostatic stepless transmission unit to the left and right traveling devices ;
An elevation drive mechanism that swings the support frame ;
Is supported by the steering handle, a work dynamic fluid tank you storing hydraulic oil in the hydrostatic continuously variable transmission unit,
And a flexible oil supply passage for connecting the hydraulic oil tank and the hydrostatic stepless transmission unit .
A walking type work in which the working unit is configured to be able to move up and down with respect to the traveling machine by integrally rocking the working unit, the engine, and the traveling mission together with the support frame with respect to the traveling machine. Machine. The walk-behind work machine according to claim 1, wherein the hydraulic oil tank is configured to allow perspective of internal hydraulic oil. The traveling mission is provided with a pair of left and right output shafts that extend in the left and right of the vehicle body and support the traveling device.
The walk type working machine according to claim 1 or 2, wherein the support frame is integrally rocked with the traveling transmission about the output shaft as an axis.

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