JP6463259B2 - Walking snowblower - Google Patents

Description

  The present invention relates to a walking type snowplow, specifically, a traveling machine body having a pair of left and right crawler traveling devices, a support frame supported by the traveling machine body so as to be able to swing up and down, and supported by the support frame, A walking type snow removal machine comprising: a snow removal part that removes snow in front of the machine body; an engine that is supported by the support frame and outputs a driving force to the snow removal part; and a lift drive mechanism that swings the support frame. About.

  In the above-described walking type snow remover, the snow removal part swings up and down with respect to the traveling machine body by swinging the support frame up and down by the lift drive mechanism, and the ground clearance of the snow removal part can be adjusted. And since the engine output to the snow removal part moves up and down together with the snow removal part, it is not necessary to provide a special accommodation structure that allows the snow removal part to be raised and lowered in the work transmission system that transmits the driving force from the engine to the snow removal part. .

  An example of this type of walking type snowplow is disclosed in Patent Document 1. That is, in the walking type snowplow shown in Patent Document 1, the rear part of the vehicle body frame is mounted on the traveling frame so as to be able to swing up and down. The vehicle body frame includes a snow removal working device and an engine. The front part of the vehicle body frame can be swung up and down by the lifting mechanism. The height of the snow removal work device can be adjusted by swinging the snow removal work device up and down together with the vehicle body frame.

JP 2010-7254 A

  In the conventional case, the rear part of the body frame that supports the engine is mounted on the traveling frame so that it can swing up and down, so that the snow removal part and the engine can be swung up and down integrally with the traveling machine body. On the other hand, in order to enable the snow removal unit and the traveling device to be driven by the same engine, the snow removal unit and the engine can swing integrally with the traveling transmission system that transmits the driving force from the engine to the crawler traveling device. A flexible structure is required.

  The present invention enables the snow removal portion and the crawler travel device to be driven by the same engine while allowing the snow removal portion and the engine to integrally swing up and down and simplifying the structure of the traveling transmission system. Provided is a walking type snow remover capable of adjusting a snow removal part by a lightweight elevating drive mechanism.

The walking type snowplow according to the present invention is:
A traveling machine body having a pair of left and right crawler traveling devices, a support frame supported by the traveling machine body so as to be swingable up and down, a snow removal unit supported by the support frame and performing snow removal work in front of the traveling machine body, An engine that is supported by a support frame and outputs a driving force to the snow removal unit; a travel mission that is supported by the support frame and that receives the output of the engine and distributes and transmits the output to the left and right crawler travel devices; An elevating drive mechanism for swinging the support frame,
The left and right crawler traveling devices include a driving wheel body supported rotatably on the front portion of the traveling machine body, a driven wheel body rotatably supported on the traveling machine body behind the driving wheel body, A crawler belt wound around the driving wheel and the driven wheel,
The support frame is supported so as to be swingable up and down with the rotation axis of the drive wheel body of the left and right crawler travel devices as a swing axis,
The elevating drive mechanism includes an electric motor as a power source, and is disposed at a position near the rear portion of the crawler belt between the left and right crawler travel devices.

  According to this configuration, when the support frame is operated to swing up and down by the lift drive mechanism, the snow removal unit swings up and down together with the support frame, and the ground clearance of the snow removal unit can be adjusted. When the ground clearance of the snow removal part is adjusted, the engine swings up and down together with the support frame, but the support frame swings up and down with the rotation axis of the drive wheel of the left and right crawler travel device as the swing axis, and is supported. Since the traveling mission swings up and down together with the frame, it is not necessary to provide a special interchangeable structure that allows the snow removal portion and the engine to swing up and down in the traveling transmission system that transmits the driving force of the engine to the left and right crawler traveling devices.

  The elevating drive mechanism applies the elevating operation force at a position away from the rotation axis of the drive wheel body to the vicinity of the rear part of the crawler belt. Therefore, the elevating drive mechanism is made small and light with an electric motor as a power source. The support frame can be smoothly swung up and down by the lift drive mechanism.

  Therefore, the left and right crawler travel devices can be driven by the engine that drives the snow removal unit while the travel transmission system has a simple structure without any special accommodation structure, and the snow removal unit is adjusted up and down by a small and lightweight lifting drive mechanism. it can.

  In the present invention, it is preferable that the lifting drive mechanism includes a pinion gear driven by the electric motor and a rack gear engaged with the pinion gear.

  According to this configuration, the rotational driving force of the electric motor can be converted into the operating force for swinging the support frame by a simple and lightweight power conversion mechanism including a pinion gear and a rack gear.

  In the present invention, it is preferable that the electric motor and the pinion gear are supported by the support frame, and the rack gear is supported by the traveling machine body.

  The member provided with the rack gear tends to be a long member that is longer in the vertical direction of the traveling machine body than the support member that supports the electric motor and the pinion gear. According to this configuration, when adjusting the height of the snow removal portion, the long member can be prevented from moving, and the elevating drive mechanism can be easily provided.

  In the present invention, it is preferable that the elevating drive mechanism is located behind the engine.

  According to this configuration, the swinging operation of the snow removal portion is controlled by swinging the support frame against the engine load, but the support frame is more than the distance from the swing axis of the support frame to the engine. Since the distance from the swing axis to the lift drive mechanism is longer, the operating force of the lift drive mechanism can be efficiently applied to the swing operation of the support frame.

  In the present invention, it is preferable that the elevating drive mechanism is located behind the rear end of the body frame of the traveling body.

  According to this configuration, the distance from the rotating shaft core of the drive wheel body to the lifting drive mechanism can be made longer than that in which the lifting drive mechanism is located in front of the rear end of the body frame, and the operating force of the lifting drive mechanism can be reduced. It is effective for the swinging operation of the support frame.

  In this invention, it is suitable when the said raising / lowering drive mechanism and a battery are located in a line with the traveling body width direction.

  According to this structure, the protrusion of the battery to the rear of the lift drive mechanism can be suppressed, and the battery is unlikely to be an obstacle to walking behind the traveling machine body.

It is a side view showing the whole walking type snowplow. It is a top view which shows the whole walking snowplow. It is a rear view which shows a raising / lowering drive mechanism and a battery. It is a diagram which shows a power transmission structure. It is a top view which shows a body frame and a support frame. It is a side view which shows a raising / lowering drive mechanism. It is a perspective view which shows a body frame. It is a top view which shows a raising / lowering operation switch. It is a rear view which shows the cooperation mechanism in a disassembled state, and the operation part of a steering clutch and a steering brake. It is a side view which shows a steering lever and an interlocking mechanism. It is a rear view which shows a steering lever and a interlocking mechanism. It is a side view which shows the steering lever in the state which entered the steering brake weakly and was operated, 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 of the grip side, and the interlocking mechanism in that state. It is explanatory drawing which shows the control system of steering operation and raising / lowering operation. It is a side view which shows the interlocking mechanism in the state which was the interlocking mechanism provided with another implementation structure, and operated the steering brake weakly. FIG. 12 is a side view showing the interlocking mechanism having another embodiment structure in a state where the steering lever is operated near the stroke end on the grip side.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a side view showing an entire walking snowplow according to an embodiment of the present invention. FIG. 2 is a plan view showing the entirety of the walking type snowplow according to the embodiment of the present invention. The direction [F] shown in FIGS. 1 and 2 is the “front side” of the traveling aircraft body, the direction [B] is the rear side of the traveling aircraft body, the direction [L] is the “left side” of the traveling aircraft body, and the direction [R] is It is defined as the “right side” of the traveling aircraft.

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

  The walking type snowplow can perform snow removal work by the snow removal unit 10 by running the traveling machine body 3. In other words, the snow removal unit 10 includes an auger housing 11 and a blower case 12 connected to the rear part of the auger housing 11. An auger 13 is supported on the auger housing 11 so as to be driven to rotate. A blower 14 is mounted in the blower case 12 so as to be driven to rotate. A shooter 15 protrudes upward from the blower case 12. The auger 13 collects snow and the shooter 15 discharges the snow collected by the blower 14 from the discharge port 15a by the jet power of the blower 14.

The traveling body 3 will be described.
As shown in FIGS. 1, 5, and 7, the body frame 1 includes a pair of left and right traveling frame body front and rear track frame portions 20 and a traveling frame body side connection frame portion 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 part 21 is a groove shape opened forward. The plane view shape of the body frame 1 is a U-shape opened forward. As shown in FIG. 5, the body frame 1 includes an empty space in which a traveling mission 30 and a support frame 75 described later are placed.

  As shown in FIG. 5, the left and right crawler travel devices 2 are distributed and supported by the left and right track frame portions 20. As shown in FIGS. 1 and 5, the left and right crawler travel devices 2 are configured such that the driving wheel body 25 is drivably supported by the front end portion of the track frame portion 20, and is positioned behind the driving wheel body 25. A driven wheel body 26 rotatably supported by the frame portion 20 and a crawler belt 27 wound around the drive wheel body 25 and the driven wheel body 26 are provided. As shown in FIG. 1, a slip-off preventing member 28 is engaged with the crawler belt 27 between the driving wheel body 25 and the driven wheel body 26. The come-off prevention 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 ends of the connecting frame portion 21. Specifically, as shown in FIGS. 5 and 7, handle support frame portions 22 are provided at the left and right ends of the connecting frame portion 21. The left and right handle support frame portions 22 project upward from the connection frame portion 21. A base portion 4 a of the steering handle 4 is supported on the handle support frame portion 22.

  The left and right handle support frame portions 22 are constituted by plate-like members. The plate-like member is attached to the connecting frame portion 21 in an attachment posture in which the plate thickness direction is the traveling body lateral width direction. The base portions 4 a of the left and right steering handles 4 are supported on the side surfaces of the handle support frame portion 22 on the lateral outer side. The left and right steering handles 4 are constituted by round pipe members. The base 4a of the left and right steering handles 4 is subjected to a press deformation process in a state where a part of the outer peripheral surface is a flat surface. The base portion 4 a is connected to the handle support frame portion 22 with a flat surface along the side surface of the handle support frame portion 22. In the present embodiment, the base portion 4a and the handle support frame portion 22 are connected by a connecting bolt. The connecting means between the base portion 4a and the handle support frame portion 22 is not limited to the connecting bolt, and welding may be employed.

  A grip portion 4 b is provided at the extended end portion of the left and right steering handles 4. The grip portions 4 b of the left and right steering handles 4 extend in the front-rear direction of the traveling machine body 3. As shown in FIG. 1, a portion between the grip portion 4 b and the base portion 4 a of the left and right steering handles 4 is connected by a pair of reinforcing rods 6 and 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 connecting with the reinforcing rods 6 and 7. An operation panel 8 is supported on the upper reinforcing bar 6.

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

  That is, the output shaft 5a is projected from the engine 5 forward. A travel clutch 31 is provided 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 constituted by a belt tension clutch. The traveling clutch 31 is not limited to a belt tension clutch, and various types of clutches such as a multi-plate friction clutch may be employed. The driving wheel bodies 25 of the left and right crawler traveling devices 2 are supported on the left and right output shafts 30L and 30R of the traveling mission 30 so as not to be relatively rotatable. The traveling mission 30 is provided with a hydrostatic continuously variable transmission 32 (hereinafter abbreviated as HST32). The HST 32 changes the driving force of the input shaft 30a by a variable displacement type axial plunger pump (not shown) and an axial plunger motor (not shown), and the driving force after the shifting is changed to the left and right output shafts 30L, 30R. To communicate.

  By switching the travel clutch 31 to the engaged state and shifting the HST 32 to the transmission state, the driving force from the engine 5 is transmitted to the left and right drive wheels 25 and the left and right crawler travel devices 2 are driven. The traveling machine body 3 can travel. By shifting the speed of the HST 32, the left and right crawler travel devices 2 are driven to switch between the forward side and the reverse side, and the forward drive speed and the reverse drive speed of the left and right crawler travel devices 2 are steplessly shifted to travel. The machine body 3 can be switched between forward and reverse, and can be continuously shifted and moved forward and backward.

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

  An operating portion (tension pulley) of the travel clutch 31 and a travel 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 swing up and down. By operating the clutch lever 33, the traveling clutch 31 can be switched to the engaged state. The traveling clutch lever 33 is configured as a deadman type. That is, the traveling clutch 31 can be maintained in the engaged state by operating the clutch lever 33, and the traveling clutch 31 is disengaged by releasing the operation of the clutch lever 33. As shown in FIGS. 1 and 2, a shift lever 34 that shifts the HST 32 is provided on the operation panel 8.

  As shown in FIG. 4, a work 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 this embodiment, the work clutch 35 is constituted by a belt tension clutch. The work clutch 35 is not limited to a belt tension clutch, and various types of clutches such as a multi-plate friction clutch may be employed.

  By switching the work clutch 35 to the engaged 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 disengaged 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.

  An operation portion (tension pulley) of the work clutch 35 and a work clutch lever 36 (see FIG. 2) 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 vertically swingable. By operating the clutch lever 36, the operation clutch 35 can be switched to the engaged state.

  As shown in FIG. 14, the traveling mission 30 is provided with a pair of left and right steering clutches 37L and 37R and a pair of left and right steering brakes 38L and 38R. The left and right steering clutches 37L and 37R include clutch ring bodies 39L and 39R. Clutch ring bodies 39L and 39R are fitted to the outer peripheral portions of the spline portions of output shafts 30L and 30R so as to be slidable and relatively non-rotatable. Claw clutch mechanisms 41L and 41R are provided across the clutch ring bodies 39L and 39R and the output gear 40. The output gear 40 is supported by the left and right output shafts 30L and 30R in a state in which the output gear 40 can be opposed to the left and right output shafts 30L and 30R. The output gear 40 is driven by the output of the HST 32. Shifters 42L and 42R are engaged with clutch ring bodies 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 mission case 44, the operation arms 45L and 45R are supported by the left and right rotation support shafts 43L and 43R so as not to be relatively rotatable.

  When the shifters 42L and 42R are swung by the swinging operation of the operation arms 45L and 45R, the clutch ring bodies 39L and 39R are moved toward the output gear 40 or are separated from the output gear 40. When the clutch ring bodies 39L and 39R are moved toward the output gear 40, the pawl clutch mechanisms 41L and 41R are operated in the engaged state. When the clutch ring bodies 39L and 39R are operated to be separated from the output gear 40, the pawl clutch mechanisms 41L and 41R are operated in a disengaged state.

  The left and right steering clutches 37L and 37R are engaged when the claw clutch mechanisms 41L and 41R are operated to be engaged, and are engaged when the claw clutch mechanisms 41L and 41R are operated to be disconnected. Become. The left and right steering clutches 37L and 37R are operated in an engaged state, thereby interlockingly connecting the output gear 40 and the output shafts 30L and 30R to transmit the output of the HST 32 to the driving wheel body 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 when the pawl clutch mechanisms 41L and 41R are operated in the disengaged state, and the crawler travel device 2 from the HST 32 is released. Cut off power transmission to.

  Left and right steering brake 38L. 38R is constituted by a multi-plate friction clutch. In the operating range where the steering clutches 37L, 37R are switched to the disengaged state, the shifters 42L, 42R are swung by the swinging operation of the operating arms 45L, 45R, so that the clutch wheels 39L, 39R are attached to the clutch. The steering brakes 38L and 38R are operated against the force spring 46, or are moved away from the steering brakes 38L and 38R.

  The left and right steering brakes 38L and 38R are turned on by being pressed by the operation portions 39a and 39b of the clutch ring bodies 39L and 39R that are operated to be shifted, and the operation portions are operated by releasing the clutch ring bodies 39L and 39R. It will be in a cutting state by releasing the press by 39a, 39b. When the left and right steering brakes 38L and 38R are in the engaged state, the left and right steering brakes 38L and 38R apply friction braking force to the output shafts 30L and 30R, and brake the crawler traveling device 2. The left and right steering brakes 38L and 38R strengthen the brake applied to the crawler traveling device 2 as the pressing force of the clutch wheel 39L39R is increased. When the left and right steering brakes 38L and 38R are turned off, the friction braking force applied to the output shafts 30L and 30R is released, and the brake applied to the crawler traveling device 2 is released.

  As shown in FIGS. 9 and 14, one actuator 49 is linked to the left and right operation arms 45 </ b> L and 45 </ b> R via a linkage 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 an electric motor, and various power sources such as a cylinder may be employed. Hereinafter, the actuator 49 will be described 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 mission case 44 via a support shaft 52. The seesaw member 51 can be oscillated with the axis of the support shaft 52 as the oscillating axis. The left and right end portions of the seesaw member 51 are connected to the left and right operation arms 45L and 45R by a pair of left and right interlocking links 53L and 53R. End portions 54L and 54R on the seesaw member side of the left and right interlocking links 53L and 53R are slidably engaged with elongated connection holes 55L and 55R of the seesaw member 51, respectively.

  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 portion 56a. Since the support shaft 52 and the connecting pin 56b are mounted across the connecting 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 are engaged with each other. The small-diameter gear 57 and the large-diameter gear 58 are interlocked and connected via the rotation support shaft 60. The large diameter gear 58 and the worm gear 59 are engaged 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 and 54R of the left and right interlocking links 53L and 53R are positioned at the arm side end portions of the connection holes 55L and 55R, and the left and right operation arms 45L and 45R are operated to the clutch engagement position by the return spring 47. Yes. 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 turn side, the seesaw member 51 is swung in the left turn direction [LS] from the neutral position [N], and the left interlocking link 53L is pulled by the seesaw member 51. Then, the left operation arm 45L is swung from the clutch engagement position toward the brake engagement position, and the left steering clutch 37L is switched to the disengaged state. When the seesaw member 51 is further swung in the left turning direction [LS] after the left steering clutch 37L is turned off, the left operating arm 45L is operated to the brake position, and the left steering brake 38L enters the on state. As the swing stroke of the seesaw member 51 in the left turning direction [LS] increases, the pressing force of the clutch wheel 39L against the left steering brake 38L increases, and the braking force of the left steering brake 38L increases. . Thus, when the left steering clutch 37L is disengaged and the left steering brake 38L is engaged, the right connecting hole 55R moves toward the right operating arm 45R, and the right steering arm 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 disconnected state.

  When the electric motor 49 is operated from the neutral state to the right turn side, the seesaw member 51 is swung in the right turn direction [RS] from the neutral position [N], and the right interlocking link 53R is moved by the seesaw member 51. When the pulling operation is performed, the right operation arm 45R is swung from the clutch engagement position toward the brake engagement position, and the right steering clutch 37R is switched to the disengaged state. When the seesaw member 51 is further swung in the right turning direction [RS] after the right steering clutch 37R is in the disengaged state, the right operating arm 45R is operated to the brake position, and the right steering is performed. The brake 38R is engaged. The larger the swing stroke of the seesaw member 51 in the right turn direction [RS], the stronger the pressing force of the clutch wheel 39R against the right steering brake 38R, and the stronger the braking force of the right steering brake 38R. Become. Thus, when the right steering clutch 37R is disengaged and the right steering brake 38R is engaged, 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 disconnected state.

  As shown in FIGS. 1 and 2, a pair of left and right steering levers 61 </ b> L and 61 </ b> R are distributed and supported on the left and right steering handles 4. Specifically, as shown in FIG. 10, a pair of left and right brackets 62 project downward from a portion in front of the grip portion 4 b of the steering handle 4. The bracket 62 and the bases of the steering levers 61L and 61R are connected via a support shaft 63. The steering levers 61 </ b> L and 61 </ b> R are lifted and swung with the shaft 63 of the support shaft 63 as the swing shaft X when operated. The steering levers 61L and 61R swing downward by the operating 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 65 </ b> L is linked to the left steering lever 61 </ b> L via the linkage mechanism 66. A right operation position detection sensor 65R is interlocked and connected to the right steering lever 61L via an 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 and 65R in conjunction with the swing of the reference stroke [A] of the steering levers 61L and 61R. The steering levers 61L and 61R and the operation position detection sensors 65L and 65R are linked and connected 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 constituted by a rotary potentiometer.

  The 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 extends from the rotation operation portions 70L and 70R of the operation position detection sensors 65L and 65R so as not to be relatively rotatable. The swing arm 68 can be swung with the rotation axis of the rotation operation portions 70L and 70R as the swing axis Y, and the operation position detection sensors 65L and 65R are operated by the swing operation.

  The interlocking member 69 extends from the part of the base of the steering levers 61L and 61R away from the swing axis X toward the inner side of the machine body. The interlocking member 69 swings integrally with the steering levers 61L and 61R using the swing axis X as the swing axis. The extended end side portion 69 a of the interlocking member 69 is engaged with the elongated connecting hole 68 a of the swing arm 68, and the interlock member 69 can slide relative to the swing arm 68 in the longitudinal direction of the swing arm. In this state, the swing arm 68 is engaged with the swing arm 68 so that the swing arm 68 can be swung. The swing axis Y of the swing arm 68 and the swing axis X of the steering levers 61L and 61R are misaligned and parallel or substantially parallel.

  When the steering levers 61L and 61R are gripped, the interlocking member 69 presses and swings the swing arm 68 by the extended end side portion 69a, and the swing arm 68 rotates the operation position detection sensors 65L and 65R. The parts 70L and 70R are rotated. As the steering levers 61L and 61R are gripped, the extending end portion 69a of the interlocking member 69 slides to the free end side of the swinging arm 68 and receives the swinging operation by the interlocking member 69. The position 68 changes to the free end side. By operating the reference stroke [A] with the steering levers 61L and 61R toward the grip end stroke end, the swing arm 68 swings by the swing angle [B] by the operation of the interlocking member 69. The closer the steering lever 61L, 61R is to the stroke end on the grip side, the greater the swing angle [B] of the swing arm 68 becomes. As the steering levers 61L and 61R approach the stroke end on the grip side, the operation position detection sensors 65L and 65R respond more sensitively to the movement of the steering levers 61L and 61R.

  That is, the operation position of the left steering lever 61L is detected by the left operation position detection sensor 65L. The operation position of the right steering lever 61R is detected by the right operation position detection sensor 65R. When the steering levers 61L and 61R are gripped by the left and right operation position detection sensors 65L and 65R, the detected operation position becomes an operation position that is displaced toward the stroke end on the grip side from the actual operation position. In this state, as the steering levers 61L and 61R are closer to the stroke end on the grip side, the detected position is detected in a state where the displacement between the detected operation position and the actual operation position becomes larger.

  As shown in FIG. 14, the left and right operation position detection sensors 65 </ b> L and 65 </ b> R and the electric motor 49 are linked to the control device 71. The control device 71 is configured using a microcomputer and includes a steering control unit 72 (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 information detected by the left and right operation position detection sensors 65L and 65R. Therefore, the electric motor 49 is controlled.

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

  When the right steering lever 61R is gripped, the steering control unit 72 moves the seesaw member 51 from the neutral position [N] to the right turning direction [RS] based on information detected by the right operation position detection sensor 65R. The electric motor 49 is controlled so that the right steering brake 38R is provided with a braking force having a strength corresponding to the detection operation position 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 the steering operation of the traveling machine body 3 can be performed.

  That is, if the left and right steering levers 61L and 61R are not gripped, the seesaw member 51 is neutralized by 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, 37R are operated to the engaged state by operating to the position [N], and the traveling machine body 3 travels straight.

  When the left steering lever 61L is grasped and operated, the seesaw member 51 is turned from the neutral position [N] to the left turning direction by the control of the electric motor 49 by the steering control unit 72 based on the detection information of the left operation position detection sensor 65L. LS] and the left steering clutch 37L is operated in the disengaged state, or the left steering brake 38L is operated in the engaged state, and the traveling machine body 3 turns leftward. When the left steering brake 38L is turned on, the left steering brake 38L is applied to the left crawler travel device 2 with a stronger braking force as the grip operation stroke of the left steering lever 61L is increased. The brake becomes stronger and the left turn radius of the traveling machine body 3 becomes smaller.

  When the right steering lever 61R is grasped and operated, the seesaw member 51 turns rightward from the neutral position [N] by the control of the electric motor 49 by the steering control unit 72 based on the detection information of the right operation position detection sensor 65R. The right steering clutch 37R is operated in the disengaged state by swinging to [RS], or the right steering brake 38R is operated in the engaged state, and the traveling machine body 3 turns to the right. When the right steering brake 38R enters the engaged state, the right steering brake 38R is applied to the right crawler traveling device 2 with a stronger braking force as the grip operation stroke of the right steering lever 61R is increased. The brake becomes stronger and the rightward turning radius of the traveling machine body 3 becomes smaller.

  As the steering levers 61L and 61R approach the stroke end on the grip side, the operation position detection sensors 65L and 65R respond more sensitively to the movements of the steering levers 61L and 61R, so that the steering brakes 38L and 38R are effective. When the steering levers 61L and 61R are slightly operated, the effectiveness of the steering brakes 38L and 38R changes only slightly and it is easy to finely adjust the braking force. At the stage where the steering brakes 38L and 38R are highly effective, the steering brakes 38L and 38R are greatly changed by slightly operating the steering levers 61L and 61R, and 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 connecting the blower case 12 to the front end of the support frame 75. The engine 5 is supported by the support frame 75 in a state of being placed on the support frame 75.

  The traveling mission 30 is supported at the lower part of the support frame 75. Specifically, as shown in FIG. 5, the traveling mission 30 has a pair of left and right cylindrical shapes that extend laterally outward from the lateral sides of the mission case 44 and have output shafts 30 </ b> L and 30 </ b> R. Output case portions 44L and 44R. The left and right output case portions 44L and 44R are supported by the lateral side portion 75a of the support frame 75, and the rear portion of the mission case 44 is supported by the rear portion 75b of the support frame 75.

  The support frame 75 is supported by the traveling machine body 3 so as to be swingable up and down with the rotation axis of the drive wheel body 25 of the left and right crawler traveling devices 2 as the swing 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 body 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 body frame 1 so as to be relatively rotatable.

  The support frame 75 includes an operation arm portion 76 that extends rearward from the rear portion of the support frame 75. An elevating drive mechanism 77 is provided across the extended end portion of the operation arm portion 76 and the body frame 1. The elevating drive mechanism 77 is driven to swing the support frame 75 up and down relative to the body frame 1, and is stopped to fix the support frame 75 to the adjusted swing position.

  By operating the lifting drive mechanism 77, the snow removal unit 10 can be adjusted up and down with respect to the traveling machine body 3, and the height of the snow removal unit 10 with respect to the ground can be adjusted. In order to adjust the height of the snow removal unit 10 to the ground, the support frame 75 swings up and down with the rotation axis of the drive wheel body 25 of the left and right crawler travel device 2 as the oscillation axis Z, and the snow removal unit 10 and the engine 5 and the traveling mission 30 integrally swing up and down with the rotational axis of the left and right drive wheel bodies 25 as the swing axis Z, so that a work transmission system that transmits driving force from the engine 5 to the snow removal unit 10; It is not necessary to provide a special accommodation structure for allowing the snow removal unit 10 to move up and down in the traveling transmission system that transmits the driving force from the engine 5 to the left and right crawler traveling devices 2. Further, even if the ground height of the snow removal unit 10 is changed, the ground posture of the traveling machine body 3 does not change, and the ground posture of the steering handle 4 does not change.

  As shown in FIGS. 3 and 14, the lift drive mechanism 77 includes a rack gear 78, a pinion gear 79, and an electric motor 80. The rack gear 78 and the pinion gear 79 are engaged with each other. An intermediate gear 79 a is supported on 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 supported by the electric motor 80 so as to be rotationally driven. The pinion gear 79 and the output gear 80a of the electric motor 80 are linked and 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 so as to protrude upward from the machine body frame 1. Specifically, a lower end portion of a member 78a including the rack gear 78 is supported by the bracket 85 via a support shaft 78b so as to be relatively rotatable. The bracket 85 is supported by the connection frame portion 21 of the body frame 1. The pinion gear 79, the intermediate gear 79a, and the electric motor 80 are supported by the support member 81. The support member 81 is supported by the rear end portion 76a of the operation arm portion 76 via the support shaft 81a so as to be relatively rotatable. 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 supported by the body frame 1. A supported configuration may be employed.

  A guide groove 82 is provided in a member 78 a including the rack gear 78. A guide pin 83 slidably engaged with the guide groove 82 is supported by the support member 81. The guide pin 83 supports a detachment preventing member 86. The come-off preventing member 86 prevents the rack gear 78 and the pinion gear 79 from separating from each other by preventing the member 78 a and the support member 81 from being separated.

  The elevating drive mechanism 77 drives the pinion gear 79 by the driving force of the electric motor 80, moves the pinion gear 79 up and down along the rack gear 78, and moves the support frame 75 up and down on the rear end side of the operation arm portion 76. Swing operation. The elevating drive mechanism 77 applies an elevating operation force to the support frame 75 at a location near the rear portion of the crawler belt 27 and away from the swing axis Z of the support frame 75 (the rotation axis of the drive wheel 25). With the small electric motor 80, the lifting / lowering adjustment of the snow removal unit 10 can be performed smoothly.

  The elevating drive mechanism 77 is disposed at a position near the rear portion of the crawler belt 27 between the left and right crawler traveling devices 2. The elevating drive mechanism 77 applies an elevating operation force at a position away from the rotational axis of the drive wheel body 25 to the vicinity of the rear part of the crawler belt 27. Therefore, the elevating drive mechanism 77 is small and light in which the electric motor 80 serves as a power source. In any case, the support frame 75 can be smoothly swung up and down by the lift drive mechanism 77.

  The lift drive mechanism 77 is located behind the engine 5. Since the lifting 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 lifting drive mechanism 77 can be efficiently applied to the swing operation of the support frame 75.

  The raising / lowering drive mechanism 77 is located behind the rear end 1r of the body frame 1. Specifically, in a state where the snow removal unit 10 has risen to the ascent limit, as shown by a solid line in FIG. 6, the entirety from the lower end to the upper end of the elevating drive mechanism 77 is located behind the rear end 1r. In the state where the snow removal unit 10 is lowered to the lower limit, as shown by a two-dot chain line in FIG. 6, the lower end side portion of the elevating drive mechanism 77 is located behind the rear end 1r. Compared with the position where the elevating drive mechanism 77 is positioned in front of the rear end 1r, the distance from the rotational axis of the drive wheel 25 to the elevating drive mechanism 77 can be increased, and the operating force of the elevating drive mechanism 77 can be used as a support frame. 75 can be efficiently operated in the swing operation. It is more preferable that the entire lifting drive mechanism 77 is positioned behind the rear end 1r regardless of the position of the lifting range from the lowering limit to the rising limit.

  As shown in FIGS. 1, 3, and 5, the elevating drive mechanism 77 and the power source battery 84 are arranged in the width direction of the traveling machine body. Protrusion of the battery 84 to the rear of the lifting drive mechanism 77 can be suppressed. In addition, the battery 84 is unlikely to be an obstacle to the inspection and repair work of the lifting drive mechanism 77 from the rear of the traveling machine body.

  As shown in FIGS. 2 and 8, the lifting operation switch 87 is supported by the right steering handle 4 in a state of being located on the inner side of the grip body 4 b of the right steering handle 4. The raising / lowering operation switch 87 is located in the site | part which can perform finger operation of the hand which supports the grip part 4b. More specifically, a boss portion 88 is provided at a position in front of the grip portion 4 b of the steering handle 4. The boss portion 88 supports the working clutch lever 36 so that it can be swung up and down. A support member 89 extends rearward from the boss portion 88. A lifting operation switch 87 is supported on the extended end of the support member 89. In this embodiment, the lifting 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 lifting operation switch 87 and the electric motor 80 are linked to the control device 71. The control device 71 includes a control unit 90 for raising and lowering (hereinafter referred to as an elevation control unit 90).

  When the operation information is input from the elevating operation switch 87, the elevating control unit 90 moves the pinion gear 79 to the ascending and descending operation positions corresponding to the operation information and stops the operation based on the input operation information. 80 is controlled.

  By pushing and operating the front end side portion of the lifting operation switch 87, the lifting control unit 90 controls the electric motor 80 to the lowering side, and the snow removal unit 10 can be lowered. By pushing and operating the rear end portion of the lifting operation switch 87, the lifting control unit 90 controls the electric motor 80 to the rising side, and the snow removal unit 10 can be lifted. While the lifting operation switch 87 is being pressed, the snow removal unit 10 continues to rise and fall unless the snow removal unit 10 reaches the stroke end.

  As shown in FIGS. 1 and 2, the headlamp 92 is supported by the traveling machine body 3. Specifically, the headlamp 92 is supported by the steering handle 4 via the upper reinforcing rod 6. The headlamp 92 is supported in a state in which the vertical adjustment in the mounting direction is possible. The headlamp 92 is displaced with respect to the shooter 15 in the lateral direction of the traveling machine body. It is possible to work while illuminating the front of the snow removal unit 10 and the like with the headlamp 92 and illuminating the shooter 15 in a state in which the shooter 15 does not easily become an obstacle to illumination. Since the headlamp 92 is supported by the traveling machine body 3 that supports the support frame 75 so as to be swingable up and down, the posture of the headlamp 92 does not change even when 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 lighting condition such as the illumination range of the headlamp 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 are communicated with each other by an oil supply path 94. The oil supply passage 94 is formed by a flexible hose and has flexibility. That is, the oil supply path 94 absorbs the change in the positional relationship between the HST 32 and the hydraulic oil tank 93 due to 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 supplied to the HST 32. The hydraulic oil tank 93 is made of a material that allows the internal hydraulic oil to be seen through. The amount of oil inside can be seen 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 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 the interlocking mechanism 66 having another embodiment structure in a state where the steering brakes 38L and 38R are weakly entered and operated. FIG. 16 is a side view showing the interlocking mechanism 66 having another embodiment structure in a state where 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 implementation structure, the interlocking member 69 is constituted by a swing link. That is, the end of the interlocking member 69 on the side of the steering lever and the part of the steering levers 61L and 61R that are separated from the swing axis X are connected via the support shaft 69b so as to be relatively rotatable. The interlocking member 69 oscillates with respect to the steering levers 61L and 61R with the axis of the support shaft 69b parallel to or substantially parallel to the oscillation axis X as the oscillation axis.

(2) In the above-described embodiment, the example in which the lifting / lowering driving mechanism 77 is provided with the rack gear 78 and the pinion gear 79 is shown. Various conversion mechanisms such as a screw mechanism that performs the above may be provided.

(3) In the above embodiment, the rack gear 78 is supported on the traveling machine body 3 and the pinion gear 79 and the electric motor 80 are supported on the support frame 75. However, the rack gear 78 is supported on the support frame 75 and the pinion gear 79 is supported. And the structure which supports the electric motor 80 to the traveling body 3 may be employ | adopted.

(4) In the above-described embodiment, the example in which the elevating drive mechanism 77 is located behind the rear end 1r of the body frame 1 is shown, but it may be arranged forward of the rear end 1r.

(5) In the above-described embodiment, the example in which the raising / lowering driving mechanism 77 and the battery 84 are arranged in the lateral width direction of the traveling machine body is shown. However, the present invention is not limited to this arrangement. Various arrangement configurations such as being positioned forward may be employed.

  The present invention is not limited to the walking type snowplow in which the steering handle 4 is provided in the traveling machine body 3 but can be applied to a walking type snowplow in which the steering handle 4 is provided in the support frame 75.

DESCRIPTION OF SYMBOLS 1 Airframe frame 1r Rear end 2 Crawler travel device 3 Traveling machine body 5 Engine 10 Snow removal part 25 Drive wheel body 26 Driven wheel body 27 Crawler belt 30 Travel mission 75 Support frame 77 Lift drive mechanism 78 Rack gear 79 Pinion gear 80 Electric motor 84 Battery Z Shaking Dynamic axis

Claims (6)

A traveling machine body having a pair of left and right crawler traveling devices, a support frame supported by the traveling machine body so as to be swingable up and down, a snow removal unit supported by the support frame and performing snow removal work in front of the traveling machine body, An engine that is supported by a support frame and outputs a driving force to the snow removal unit; a travel mission that is supported by the support frame and that receives the output of the engine and distributes and transmits the output to the left and right crawler travel devices; An elevating drive mechanism for swinging the support frame,
The left and right crawler traveling devices include a driving wheel body supported rotatably on the front portion of the traveling machine body, a driven wheel body rotatably supported on the traveling machine body behind the driving wheel body, A crawler belt wound around the driving wheel and the driven wheel,
The support frame is supported so as to be swingable up and down with the rotation axis of the drive wheel body of the left and right crawler travel devices as a swing axis,
The elevating drive mechanism includes an electric motor as a power source, and is a walking type snowplow disposed at a position near the rear portion of the crawler belt between the left and right crawler travel devices.   The walking type snowplow according to claim 1, wherein the elevating drive mechanism includes a pinion gear driven by the electric motor and a rack gear engaged with the pinion gear.   The walking type snowplow according to claim 2, wherein the electric motor and the pinion gear are supported by the support frame, and the rack gear is supported by the traveling machine body.   The walking type snow remover according to any one of claims 1 to 3, wherein the elevating drive mechanism is located behind the engine.   The walking type snow remover according to any one of claims 1 to 4, wherein the elevating drive mechanism is located rearward of a rear end of a body frame of the traveling machine body.   The walking type snow remover according to any one of claims 1 to 5, wherein the elevating drive mechanism and the battery are arranged in a lateral direction of the traveling machine body.

Images