JP2022083575A - Walking type working machine - Google Patents

Abstract

To achieve high turning performance in a constitution having a crawler unit for moving a machine body.SOLUTION: A transplanter 1 configured as a walking type working machine, includes: crawler units 30; chain cases 37 supported on a machine body 6; and links 90 each constituting a link mechanism interlocking with a lifting operation of the machine body 6 along with the chain case 37. The crawler unit 30 includes: a drive sprocket 61 supported on an axle 39 mounted on the chain case 37; a track roller 62; and a crawler 63 wound therearound. The link mechanism 60 includes an axial center position of the axle 39 in a joint and is constituted to ascend/descend the track roller 62 accompanied with rotational operation of the machine body 6 about the axle 39, with the crawler unit 30 grounded.SELECTED DRAWING: Figure 1

Description

The present invention relates to a walking work machine that is moved by a walking worker, such as a transplant machine or a management machine.

Conventionally, as an agricultural work machine such as a porting machine, a management machine, or a rice transplanter, there is a walking type work machine in which a worker moves the machine while walking. Some walking-type work machines are provided with a crawler unit in which a crawler, which is a trackless crawler, is wound around a wheel such as a sprocket as a traveling unit for moving the machine.

Patent Document 1 has a swing case in which a transmission chain is incorporated and one end of which is pivotally supported by a horizontal axis so as to swing up and down, and a drive wheel of a crawler unit is pivotally supported at the other end of the swing case. A rice transplanter having a configuration is disclosed. The crawler unit has a driven wheel that receives the winding of the crawler together with the drive wheel on the rear side of the drive wheel pivotally supported at the other end of the swing case.

In Patent Document 1, the swing case that supports the drive wheels of the crawler unit constitutes a parallel link mechanism together with a link having the same length as the swing case and a connecting rod having one end side supported by the axle of the drive wheels. That is, the crawler unit is attached to the machine body via a parallel link mechanism including a swing case. With such a configuration, the crawler unit maintains a horizontal state in raising and lowering the machine body accompanied by rotation of the swing case.

Jikkai Sho 55-9419

According to the configuration disclosed in Patent Document 1, since the crawler unit maintains a horizontal state, the entire portion of the crawler on the ground contact surface side from the lower side of the drive wheel to the lower side of the driven wheel is the road surface of the field. It will be in a grounded state. Therefore, it is difficult to obtain good turning performance when the aircraft is turning.

The present invention has been made in view of the above-mentioned problems, and provides a walking work machine capable of obtaining good turning performance in a configuration having a crawler unit for moving the machine body. The purpose.

The walking type working machine according to the present invention is a walking type working machine that is moved by a walking worker, and includes a crawler unit for moving the machine body, a transmission case supported by the body, and the transmission case. The crawler unit includes a link constituting a link mechanism interlocking with the elevating operation of the machine body, and the crawler unit includes a drive wheel supported by an axle provided in the transmission case, a driven wheel, the drive wheel, and the driven wheel. The link mechanism includes the axial center position of the axle at the node, and the crawler unit is in contact with the ground to rotate the aircraft around the axle. Therefore, it is configured to raise and lower the driven wheel.

Further, in the walking type working machine according to another aspect of the present invention, in the walking type working machine, the driven wheel is arranged in front of the driving wheel, and the link mechanism is in a state where the crawler unit is grounded. The driven wheel is configured to be separated from the ground by rotating the machine body about the axle so as to move backward.

Further, the walking type working machine according to another aspect of the present invention is the walking type working machine, in which the link is directed in a direction in which the nodes of the link mechanism located at both ends of the link are brought close to each other and separated from each other in a side view. It has a shock absorber.

According to the present invention, good turning performance can be obtained in a configuration including a crawler unit for moving the airframe.

It is a left side view which shows the state which raised the body of the transplantation machine which concerns on one Embodiment of this invention. It is a left side view which shows the state which the machine body of the transplantation machine which concerns on one Embodiment of this invention is lowered. It is a top view which shows the structure of the undercarriage of the transplantation machine which concerns on one Embodiment of this invention. It is a front perspective view which shows the structure of the undercarriage of the transplantation machine which concerns on one Embodiment of this invention. It is a top view which shows the structure of the left half part of the undercarriage of the transplantation machine which concerns on one Embodiment of this invention. It is a left side view which shows the structure of the crawler unit which concerns on one Embodiment of this invention, and its periphery. It is a front perspective view which shows the structure of the crawler unit which concerns on one Embodiment of this invention, and its periphery. It is a front view which shows the stopper mechanism which the link which concerns on one Embodiment of this invention has. It is a left side view which shows the state which the machine body of the transplantation machine which concerns on one Embodiment of this invention is tilted backward. It is a top view which shows the structure of the left half part of the undercarriage in the state which the crawler unit of the transplanter which concerns on one Embodiment of this invention is replaced. It is a right side view which shows the structure of the crawler unit in the state which replaced the crawler unit which concerns on one Embodiment of this invention, and the periphery thereof. It is a side view which shows the structure of the crawler unit which concerns on another Embodiment of this invention. It is a side view which shows the structure of the drive sprocket which concerns on another Embodiment of this invention. It is a perspective view which shows a part of the drive sprocket which concerns on another Embodiment of this invention. It is a side view which shows the modification of the drive sprocket which concerns on another Embodiment of this invention.

The present invention is a walking type work machine having a crawler unit as a traveling unit for moving the machine, by devising a configuration of a link mechanism for connecting the crawler unit and the crawler unit to the machine, thereby turning performance of the machine. It is intended to improve. Hereinafter, embodiments of the present invention will be described.

In the present embodiment, as a walking type working machine, a transplanting machine for transplanting seedlings to ridges in a field will be described as an example. However, the present invention can be applied not only to a transplanting machine but also to other walking type working machines such as a management machine and a rice transplanter.

As shown in FIGS. 1 and 2, the transplanting machine 1 according to the present embodiment is a walking type vegetable transplanting machine that is moved by a walking worker. In the transplant machine 1, the forward direction (left direction in FIG. 1) of the transplant machine 1 is the front, and the opposite direction (right direction in FIG. 1) is the rear, and the left and right directions are facing forward. To the left and right, respectively.

The transplanting machine 1 takes out the cell-molded seedlings and transplants them into the ridges of the field while moving forward by the operation of the operator. The transplanting machine 1 includes a traveling machine 2, a seedling supply unit 3 provided behind the traveling machine 2, a transplanting unit 4 provided between the traveling machine 2 and the seedling supply unit 3, and a seedling supply unit 3. It is provided with a control unit 5 provided at the rear.

The traveling machine body 2 has a machine body 6 forming a main body portion thereof and a traveling unit 7 for moving the machine body 6. The airframe 6 has an airframe 8 having a frame structure thereof, an engine 9 mounted on the front part of the airframe 8, and a mission case 10 supported by the rear part of the airframe 8. The upper side of the engine 9 is covered with the bonnet 11. The mission case 10 is provided at the left and right center portions in the rear portion of the machine body 6 in a state of being fixed to the machine body 6. The transplant portion 4 is supported on the rear side of the machine frame 8.

At the rear end of the airframe frame 8, a pair of left and right operation unit frames 12 arranged in an inclined shape that rises rearward in a side view are provided. On the upper side of the left and right operation unit frames 12, handles 13 having a substantially "U" shape in a plan view are provided. In the control unit 5, in the handle 13 and its vicinity, a main shift lever for shifting the traveling speed of the traveling machine body 2, a planting clutch lever for turning on / off the planting clutch, and an up / down of the machine body 6 are performed. An operation unit 15 is provided in which various operation tools such as the elevating lever 14 of the above are arranged.

The seedling supply unit 3 supplies the cell-shaped seedlings housed in the seedling tray 20 to the transplant unit 4. The seedling tray 20 is made of a flexible synthetic resin, and a concave pot portion 20a for accommodating a plurality of cell-molded seedlings is continuously formed in the vertical direction and the horizontal direction.

The seedling supply unit 3 is configured by attaching a tray mounting table 22, an empty tray storage table 23, and a vertical transport device 24 to a transport frame 21 formed by bending a pipe so as to form a substantially "U" shape in a plan view. Has been done. The tray mounting table 22 is for mounting the seedling tray 20, and is provided so as to be inclined from the front low to the rear height in a side view.

The empty tray storage table 23 is for placing an empty seedling tray 20 after transplanting under the tray mounting table 22, and is formed by bending a rod-shaped body from the front lower part to the upper rear part of the vertical transfer device 24. It has been extended toward. The vertical transfer device 24 is configured to reciprocate left and right by power from a planting mission case (not shown), transmits the power from the planting mission case to the drive shaft 24a, and vertically feeds the seedling tray 20.

The vertical transfer device 24 intermittently feeds the seedling tray 20 laterally in the cell-molded seedling take-out operation by the seedling take-out device 25, and when the cell-molded seedling take-out operation of one horizontal row is completed, the cell molding of the next row is completed. In order to take out the seedlings, the seedling tray 20 is vertically fed one step. The vertical feed operation of the seedling tray 20 in the vertical transfer device 24 is performed by using the rotational driving force of the drive shaft 24a.

The transplanting unit 4 is provided in front of the vertical transfer device 24, and the cell-shaped seedlings supplied from the seedling supply unit 3 are transplanted to the ridges. The transplanting unit 4 includes a seedling extraction device 25 and a seedling transplanting device 26. The seedling extraction device 25 and the seedling transplanting device 26 are configured to be driven by power from a planting mission case (not shown).

The seedling extraction device 25 takes out cell-formed seedlings from the pot portion 20a of the seedling tray 20 placed on the tray mounting table 22 of the seedling supply unit 3 by means of a seedling extraction claw (not shown) and directs them downward in the seedling transplanting device 26. It is released and supplied to the seedling transplanting claw 26a which is provided so as to protrude and is configured to be openable and closable. The seedling transplanting device 26 conveys the cell-formed seedlings in the seedling transplanting claw 26a to the upper surface of the ridge, opens the seedling transplanting claw 26a, and transplants (plants) the seedling transplanting claw 26a into the ridge. After transplanting the cell-formed seedlings, the soil at the roots of the planted seedlings is pressed from both the left and right sides by a pair of left and right suppression rings 27 provided below the rear of the seedling transplanting device 26.

As described above, the transplanting machine 1 takes out the cell-formed seedlings from the seedling tray 20 and transplants them onto the ridges in the transplanting unit 4 while performing the horizontal feeding operation and the vertical feeding operation of the seedling tray 20 in the seedling supply unit 3. do.

As shown in FIGS. 3 and 4, the traveling unit 7 includes left and right front wheels 31 provided on the lower side of the front part of the machine body 6 and left and right crawler units 30 provided on the lower side of the rear part of the machine body 6. Has. The traveling portion 7 is configured symmetrically or substantially symmetrically with respect to the left and right front wheels 31, the left and right crawler units 30, and the support configurations thereof.

The front wheel 31 is rotatably supported with the left-right direction as the rotation axis direction by the front wheel support frame 32 extending in the left-right outward direction from the lower side of the vicinity portion of the front end portion of the airframe frame 8. The front wheel support frame 32 extends from the front wheel support shaft portion 33 rotatably supported with respect to the airframe frame 8 in the left-right direction and the left and right outer ends of the front wheel support shaft portion 33 toward the rear side. It has a front wheel support arm 34 that is exposed, and is configured to form a substantially "L" shape in a plan view. The front wheel 31 is supported by a support shaft 34a provided at the rear end of the front wheel support arm 34 with the left-right direction as the axial direction.

The front wheel support shaft portion 33 has a tubular outer pipe portion 33a having a hexagonal cross-sectional shape and an insertion shaft portion 33b having a hexagonal cross-sectional shape and inserted into the outer pipe portion 33a. The insertion shaft portion 33b is inserted and supported with respect to the outer pipe portion 33a so as to be non-rotatable and movable in the axial direction due to the insertion structure having a hexagonal cross section with respect to the outer pipe portion 33a. The left and right outer portions of the insertion shaft portion 33b are exposed from the outer pipe portion 33a, and the front wheel support arm 34 is fixedly fixed to the left and right outer ends of the insertion shaft portion 33b by welding or the like. That is, the insertion shaft portion 33b and the front wheel support arm 34 form an integral support member that can move in the left-right direction in a substantially "L" shape in a plan view.

The movement of the insertion shaft portion 33b with respect to the outer pipe portion 33a is restricted by the shaft fixing portion 35 provided on the front wheel support shaft portion 33. The shaft fixing portion 35 has a fixing pin 35a screwed into the peripheral wall of the outer pipe portion 33a, and an operation handle 35b for rotating the fixing pin 35a by penetrating the fixing pin 35a in the radial direction. The fixing pin 35a penetrates the peripheral wall of the outer pipe portion 33a and abuts on one side surface of the hexagonal columnar outer shape of the insertion shaft portion 33b to restrict the axial movement of the insertion shaft portion 33b.

With the front wheel support shaft portion 33 having such a configuration, the position in the left-right direction of the front wheel 31, that is, the tread of the left and right front wheels 31 can be adjusted by adjusting the axial position of the insertion shaft portion 33b with respect to the outer pipe portion 33a. (See Fig. 3, arrow A1).

The left and right crawler units 30 are provided in a state of being supported by chain cases 37 provided on the left and right outer sides of the mission case 10. The chain case 37 is connected to the left and right outer ends of the cylindrical drive shaft case 36 that extends linearly from the mission case 10 in the left and right outward directions. The drive shaft case 36 is rotatably provided with respect to the mission case 10 with the left-right direction as the rotation axis direction. Inside the drive shaft case 36, a crawler drive shaft 38 extending from the mission case 10 in the left-right outward direction and having the left-right direction as the axial direction is provided.

The chain case 37 has a substantially plate-like outer shape with the left-right direction as the plate thickness direction, and the front-rear direction as the longitudinal direction in a plan view. Further, the chain case 37 has an arm-shaped outer shape in which both ends in the longitudinal direction are rounded in a semicircular shape in a side view.

The chain case 37 has a front end portion on one end side in the longitudinal direction connected to the drive shaft case 36 via a connecting member 29, and is driven around the axis P1 (see FIG. 6) of the crawler drive shaft 38. It is provided so as to rotate integrally with the shaft case 36. The connecting member 29 is fixed to the drive shaft case 36 in a state of being fitted to the left and right outer openings of the cylindrical drive shaft case 36. The connecting member 29 has a projecting piece portion 29a protruding outward from the fitting portion with respect to the drive shaft case 36. On the other hand, the front end portion of the chain case 37 is provided with a projecting piece portion 37a projecting in an angular shape toward the upper part of the oblique front. The projecting piece portion 37a of the chain case 37 is fixed to the projecting piece portion 29a of the connecting member 29 by a fixing tool such as a bolt 28.

In this way, the chain case 37 is fixed to the drive shaft case 36 via the connecting member 29 at its front end. As a result, the chain case 37 is provided integrally with the drive shaft case 36 so as to be rotatable around the axis P1 with the left-right direction as the rotation axis direction. That is, the chain case 37 is provided so as to be able to swing up and down so as to move the rear side up and down with the axis P1 located at the front end thereof as the center.

Further, the chain case 37 is provided so that the position can be adjusted in the left-right direction (see FIG. 3, arrow A2). For example, the chain case 37 is provided so as to be movable relative to the drive shaft case 36 in the left-right direction at a portion supported by the connecting member 29 with respect to the drive shaft case 36. Then, in the support portion of the chain case 37 with respect to the drive shaft case 36, the position of the chain case 37 in the left-right direction with respect to the drive shaft case 36 is determined by the presence or absence of a ring-shaped spacer (not shown) that penetrates the crawler drive shaft 38. Adjustments are made.

Inside the chain case 37, a chain transmission mechanism for transmitting the rotational power of the crawler drive shaft 38 provided in the drive shaft case 36 to the crawler unit 30 is provided. The chain transmission mechanism in the chain case 37 includes a drive sprocket fixed to the crawler drive shaft 38 and a driven sprocket fixed to the axle 39 rotatably supported at the rear end of the chain case 37. Includes a chain wound around a sprocket. The crawler unit 30 is connected to the chain case 37 by an axle 39.

With such a configuration, the power from the engine 9 is transmitted from the transmission case 10 to the crawler drive shaft 38 in the drive shaft case 36, and further, the crawler unit 30 is transmitted via the chain transmission mechanism in the chain case 37 and the axle 39. Is transmitted to. The crawler unit 30 is driven by the rotational driving force of the axle 39.

Next, a configuration for raising and lowering the machine body 6 in the transplanting machine 1 will be described. The elevating operation of the machine body 6 is relative to the front wheel 31 and the crawler unit 30 in a state of being in contact with the ground G1 by raising and lowering the left and right front wheels 31 and the left and right crawler units 30 that support the machine body 6 with respect to the machine body. It is done as an operation.

The transplant machine 1 includes a hydraulic pump 40, a lifting cylinder 41 which is a hydraulic cylinder mechanism, a swing fulcrum shaft 42, left and right swing rods 43, and left and right connecting rods 44 as a configuration for raising and lowering the machine body 6. Be prepared. The elevating operation of the machine body 6 is performed by operating the elevating cylinder 41 by switching the hydraulic elevating valve provided for the hydraulic pump 40. The hydraulic pump 40 is mounted on the front side of the engine 9 on the front end portion of the airframe frame 8 (see FIG. 1).

The elevating cylinder 41 is provided at the center of the left and right sides of the machine body 6 at a position above the rear portion of the mission case 10 so as to be along the front-rear direction in a plan view. The elevating cylinder 41 is provided in an inclined shape that descends forward, and the expansion / contraction direction is the inclined direction that descends forward in a side view.

The elevating cylinder 41 has a cylinder portion 41a and a piston portion 41b provided so as to be reciprocally movable with respect to the cylinder portion 41a, and expands and contracts due to the reciprocating movement of the piston portion 41b with respect to the cylinder portion 41a. The elevating cylinder 41 is provided with the cylinder portion 41a as a fixing portion to the machine body 6 with the piston portion 41b side facing the rear side. The elevating cylinder 41 operates by the hydraulic pressure supplied from the hydraulic pump 40. A swing fulcrum shaft 42 is provided on the rear side of the elevating cylinder 41.

The swing fulcrum shaft 42 is provided at a position above the rear portion of the mission case 10 in the left-right central portion of the machine body 6 with the left-right direction as the axial direction. The swing fulcrum shaft 42 is provided in a state in which both ends thereof are projected from the shaft case 42a while being fitted into the tubular shaft case 42a whose left-right direction is the cylindrical shaft direction so as to be relatively rotatable. The swing fulcrum shaft 42 is provided as a movable shaft in the machine body 6. The swing fulcrum shaft 42 moves integrally with the shaft case 42a as the elevating cylinder 41 expands and contracts.

The shaft case 42a is connected to the rear side of the piston portion 41b of the elevating cylinder 41 at the connecting plate portion 42b provided at the central portion in the axial direction thereof. A plate-shaped flange portion 41c that overlaps the connecting plate portion 42b is provided at the rear end portion of the piston portion 41b, and the connecting plate portion 42b and the flange portion 41c are fixed to each other by bolts or the like, so that the piston portion 41b Is fixed to the shaft case 42a. With such a configuration, the swing fulcrum shaft 42 moves integrally with the piston portion 41b and the shaft case 42a as the elevating cylinder 41 expands and contracts.

Of the left and right swing rods 43, the left swing rod 43L located on the left side rotates its rear end in the left-right direction with respect to the left support flange portion 42c provided at the left end of the swing fulcrum shaft 42. It is rotatably connected as. The left support flange portion 42c projects upward with respect to the axial center position of the swing fulcrum shaft 42, and supports the rear end portion of the left swing rod 43L at a position above the axial center of the swing fulcrum shaft 42. ing.

On the other hand, the right swing rod 43R located on the right side rotatably connects the rear end portion to the right support flange portion 42d provided at the right end portion of the swing fulcrum shaft 42 with the left-right direction as the rotation axis direction. I'm letting you. The right support flange portion 42d projects downward with respect to the axial center position of the swing fulcrum shaft 42, and supports the rear end portion of the right swing rod 43R at a position below the axial center of the swing fulcrum shaft 42. is doing.

The front end portions of the left and right swing rods 43 are rotatably connected to the support projecting piece portion 36a projecting from the drive shaft case 36 with the left-right direction as the rotation axis direction. The support projecting piece portion 36a is a part of the drive shaft case 36 and is a plate-shaped portion having a plate thickness direction in the left-right direction, and is projected from the outer peripheral surface portion of the drive shaft case 36 toward the diagonally front and upper direction. ing. The support projecting piece portion 36a supports the front end portion of the swing rod 43 at the upper end portion thereof.

The left and right connecting rods 44 have their rear end portions rotatably connected to the support projecting piece portion 36a with the left-right direction as the rotation axis direction. The rear end portion of the connecting rod 44 is supported by a portion (on the base side of the support protrusion portion 36a) below the shaft support portion of the front end portion of the swing rod 43 in the support protrusion portion 36a.

The front end portions of the left and right connecting rods 44 are rotatably connected to the support arm portion 33c provided on the outer pipe portion 33a of the front wheel support shaft portion 33 with the left-right direction as the rotation axis direction. The support arm portion 33c projects upward with respect to the axial center position of the front wheel support shaft portion 33, and supports the front end portion of the connecting rod 44 at a position above the axial center of the front wheel support shaft portion 33. There is.

With the above configuration, the machine body 6 moves up and down by the expansion and contraction operation of the elevating cylinder 41. That is, as the elevating cylinder 41 extends, the swing fulcrum shaft 42 moves to the rear side, and the support projecting piece portion 36a is pulled to the rear by the swing rod 43. As a result, the drive shaft case 36 and the chain case 37 rotate integrally around the axis of the crawler drive shaft 38. Here, the chain case 37 rotates in the direction of lowering the rear side, that is, in the direction of lowering the crawler unit 30 relative to the machine body 6.

Further, when the support projecting piece portion 36a is pulled backward by the swing rod 43, the support arm portion 33c is pulled backward by the connecting rod 44, and the front wheel support shaft portion 33 lowers the front wheel support arm 34, that is, the airframe 6. The front wheel 31 is rotated so as to be relatively lowered. Such downward movement of the crawler unit 30 and the front wheel 31 with respect to the airframe 6 is an ascending operation of the airframe 6.

On the other hand, as the elevating cylinder 41 contracts, the swing fulcrum shaft 42 moves to the front side, and the support projecting piece portion 36a is pushed forward by the swing rod 43. As a result, the drive shaft case 36 and the chain case 37 rotate integrally around the axis of the crawler drive shaft 38. Here, the chain case 37 rotates in the direction of raising the rear side, that is, in the direction of raising the crawler unit 30 relative to the machine body 6.

Further, when the support projecting piece portion 36a is pushed forward by the swing rod 43, the support arm portion 33c is pushed forward by the connecting rod 44, and the front wheel support shaft portion 33 raises the front wheel support arm 34, that is, the airframe 6. The front wheel 31 is rotated in a direction of relatively raising the front wheel 31. Such upward movement of the crawler unit 30 and the front wheel 31 with respect to the airframe 6 is a descending motion of the airframe 6.

The elevating operation of the machine body 6 as described above is performed by operating the elevating lever of the operation unit 15. That is, the elevating lever is connected to the hydraulic elevating valve via a predetermined operating member, the hydraulic elevating valve is operated by the operation of the elevating lever, and the elevating cylinder 41 is operated by the hydraulic pressure supplied from the hydraulic pump 40.

Further, regarding the raising / lowering operation of the machine body 6, the control for raising / lowering the machine body 6 is performed so as to keep the planting depth by the transplanting portion 4 constant. Specifically, the compression wheel 27 is connected to the hydraulic lift valve via a predetermined sensor member, and the operation of the compression ring 27 that moves up and down due to the unevenness of the ridge operates the hydraulic lift valve via the sensor member. The hydraulic pressure supplied from the hydraulic pump 40 to the elevating cylinder 41 is controlled. As a result, the ascending / descending motion of the machine body 6 is controlled so that the height of the machine body 6 is maintained at a constant value according to the vertical movement of the compression wheel 27 following the unevenness of the ridge.

Further, the airframe 6 is configured to be inclined to the left and right. The tilting operation of the airframe 6 is performed by raising one of the left and right crawler units 30 and the front wheels 31 and lowering the other left and right crawler units 30 and the front wheels 31.

The transplanting machine 1 includes a rolling cylinder 51, which is a hydraulic cylinder mechanism, as a configuration for tilting the machine body 6 to the left and right. The tilting operation of the machine body 6 is performed by operating the rolling cylinder 51 by switching a predetermined valve mechanism provided for the hydraulic pump 40.

The rolling cylinder 51 is provided at a position on the right side of the elevating cylinder 41 so as to be along the front-rear direction in a plan view. The rolling cylinder 51 is provided in parallel with the elevating cylinder 41, and the expansion / contraction direction is the same as that of the elevating cylinder 41, which is a downward tilting direction in the side view.

The rolling cylinder 51 has a cylinder portion 51a and a piston portion 51b provided so as to be reciprocally movable with respect to the cylinder portion 51a, and expands and contracts due to the reciprocating movement of the piston portion 51b with respect to the cylinder portion 51a. The rolling cylinder 51 is provided with the piston portion 51b facing the rear side and the cylinder portion 51a being supported by a cylinder stay 52 provided on the right side of the elevating cylinder 41. The cylinder stay 52 is a portion integrated with the shaft case 42a, and rotatably supports the cylinder portion 51a by a shaft member such as a pin whose axial direction is the left-right direction. The rolling cylinder 51 is operated by the hydraulic pressure supplied from the hydraulic pump 40.

The rolling cylinder 51 rotatably connects the tip end portion of the piston portion 51b to the rolling arm portion 42e provided on the right side portion of the swing fulcrum shaft 42 with the left-right direction as the rotation axis direction. .. The rolling arm portion 42e is located to the left of the right support flange portion 42d, projects upward with respect to the axial center position of the swing fulcrum shaft 42, and is located above the axial center of the swing fulcrum shaft 42. Supports the rear end of the piston portion 51b.

With the above configuration, the machine body 6 is tilted to the left and right by the expansion and contraction operation of the rolling cylinder 51. That is, as the rolling cylinder 51 extends, the rolling arm portion 42e is pushed to the rear side, and the swing fulcrum shaft 42 rotates clockwise in the left side view. As a result, the left swing rod 43L connected to the left support flange portion 42c protruding upward from the swing fulcrum shaft 42 is pulled backward, and the right connected to the right support flange portion 42d protruding downward from the swing fulcrum shaft 42. The swing rod 43R is pushed forward.

By operating the left and right swing rods 43 in opposite directions in this way, the left side of the machine 6 is raised by the crawler unit 30 and the front wheel 31 on the left side that move downward relative to the machine 6, and the left side of the body 6 is raised with respect to the body 6. The right side of the airframe 6 is lowered by the crawler unit 30 on the right side and the front wheel 31 that move relatively upward. That is, the aircraft 6 is tilted so as to lower the right side.

On the other hand, as the rolling cylinder 51 contracts, the rolling arm portion 42e is pulled forward and the swing fulcrum shaft 42 rotates counterclockwise in the left side view. As a result, the left swing rod 43L is pushed forward, the right swing rod 43R is pulled backward, and contrary to the case where the rolling cylinder 51 is extended, the left side of the machine body 6 is lowered and the right side is raised, and the machine body 6 is raised. Tilt to lower the left side.

With respect to the tilting operation of the machine body 6 as described above, control is performed so that the machine body 6 is automatically tilted so that the machine body 6 remains in a horizontal state even if the machine body 6 is tilted due to unevenness or inclination of the field. Specifically, it is as follows. A rolling weight that tilts together with the machine body 6 is provided on the front side of the hydraulic pump 40 on the front end portion of the machine body frame 8. A predetermined sensor member that operates with the inclination of the rolling weight is connected to a rolling spool provided in the hydraulic pump 40. The rolling spool operates a control valve provided for the hydraulic pump 40.

With such a configuration, the machine body 6 is tilted due to unevenness or inclination of the field, and the rolling weight is tilted, so that the rolling spool operates via the sensor member and the control valve operates according to the direction of the inclination. As a result, pressure oil is supplied from the hydraulic pump 40 to the rolling cylinder 51 via a predetermined valve mechanism, the rolling cylinder 51 expands and contracts, and the machine 6 rolls left and right until the machine 6 is in a horizontal state. The tilting operation of the machine body 6 is also manually performed by operating the lever for tilting the machine body provided in the operation unit 15.

As described above, the transplanting machine 1 according to the present embodiment has a crawler unit 30 for moving the machine body 6 and a chain as a transmission case rotatably supported in the left-right direction with respect to the machine body 6. A case 37 is provided. The porting machine 1 has been devised in terms of the structure of the undercarriage in order to improve the turning performance of the machine body 6.

The crawler unit 30 of the transplanting machine 1 and the supporting configuration thereof according to the present embodiment will be described with reference to FIGS. 3 to 11. 6 and 7 show the crawler unit 30 on the left side of the left and right sides and the support configuration thereof.

The transplanting machine 1 includes a link mechanism 60 provided between the machine 6 side and the crawler unit 30 and interlocked with the raising and lowering operation of the machine 6. The link mechanism 60 includes a chain case 37 and a link 90 provided between the machine body 6 side and the crawler unit 30.

The chain case 37 is supported on the machine body 6 side by being supported by the drive shaft case 36 with respect to the mission case 10 mounted on the machine body 6. The crawler unit 30 is supported by the axle 39 with respect to the chain case 37 supported on the machine body 6 side in this way, and the crawler unit 30 is further supported by the link 90 with respect to the machine body 6 side. In this way, the link mechanism 60 is configured by the chain case 37 and the link 90 that support the crawler unit 30 with respect to the machine body 6.

The crawler unit 30 will be described. The crawler unit 30 includes a drive sprocket 61 which is a drive wheel provided on the rear end side which is the other end side of the chain case 37 and is supported by an axle 39 whose axial direction is the left-right direction, and a rolling wheel 62 which is a driven wheel. It has a drive sprocket 61 and a crawler 63 wound around a wheel 62.

The drive sprocket 61 is connected to the axle 39 in a fixed state. The drive sprocket 61 includes a hub portion 65 which forms a central portion thereof and receives an axle 39 connected to the hub portion 65, a plurality of spoke portions 66 formed radially around the central axis of the drive sprocket 61 from the hub portion 65, and a drive sprocket 61. It has a rim portion 67 forming the outer edge of the. The central axis of the drive sprocket 61 coincides with the axle center O1 which is the axis of the axle 39.

The drive sprocket 61 is configured to form a hub portion 65, a spoke portion 66, and a rim portion 67 as an integral member having a predetermined thickness with the left-right direction as the thickness direction. On the outer peripheral side of the rim portion 67, a plurality of tooth portions 68 serving as engagement portions with the crawler 63 are provided at predetermined intervals in the circumferential direction. The tooth portions 68 are formed so as to form a mountain shape toward the outside in the radial direction in the central axial direction of the drive sprocket 61.

Like the drive sprocket 61, the wheel 62 is a wheel whose left-right direction is the rotation axis direction, and is arranged in front of the drive sprocket 61. The wheel 62 is smaller than the drive sprocket 61. The outer diameter of the rolling wheel 62 is, for example, about 1/3 to 1/2 of the outer diameter of the drive sprocket 61.

The rolling wheel 62 has a first wheel portion 62a and a second wheel portion 62b which are substantially disk-shaped portions having the same diameter, and an intermediate shaft portion 62c which is a small diameter portion connecting the central portions of these wheel portions. .. The first wheel portion 62a, the second wheel portion 62b, and the intermediate shaft portion 62c constitute a rolling wheel 62 which is an integral rotating body.

In the wheel 62, the first wheel portion 62a is located on the left and right outside, and the second wheel portion 62b is located on the left and right inside. With respect to the rolling wheel 62, the drive sprocket 61 has its front end positioned between the first wheel portion 62a and the second wheel portion 62b. That is, the wheel 62 overlaps the rear portion with the front end portion of the drive sprocket 61 in the rotation axis direction view (side view). The rolling wheel 62 may be provided at a position where it does not overlap with the drive sprocket 61 in a side view.

The wheel 62 is supported via a support flange portion 70 provided for the drive sprocket 61 and a wheel damper mechanism 71.

The support flange portion 70 is provided on the left and right outer sides of the drive sprocket 61 so as to be within the range of the outer shape of the drive sprocket 61 in a side view. The support flange portion 70 has a plate-shaped portion having a substantially fan-shaped side view as a main body portion while the left-right direction is the plate thickness direction.

The support flange portion 70 has a substantially fan-shaped central angle side in a side view facing the rolling wheel 62 side. In the present embodiment, the side view shape formed by the support flange portion 70 is a substantially fan shape having a central angle of about 30 to 40 °. The support flange portion 70 has a bent surface portion 70a that is bent inward to the left and right with respect to the main body portion along the upper and lower linear edge portions corresponding to the radius of the substantially fan shape that is the side view shape.

The support flange portion 70 is rotatably supported with respect to the tubular shaft portion 72 fixed to the hub portion 65 of the drive sprocket 61. The cylinder shaft portion 72 has its central axis aligned with the axle center O1 and projects from the hub portion 65 of the drive sprocket 61 toward the left and right outwards. The cylinder shaft portion 72 supports the support flange portion 70 in a state of penetrating the circular support hole portion formed in the central portion of the support flange portion 70. A retaining ring 73 for retaining the cylinder shaft portion 72 is attached to the protruding portion of the cylinder shaft portion 72 from the support flange portion 70 in a state of being outerly fitted in the outer peripheral groove.

As shown in FIG. 6, the support flange portion 70 has a line-symmetrical shape with a predetermined straight line L1 passing through the axle center O1 corresponding to the center of the support hole portion penetrating the tubular shaft portion 72 as the center line in a side view. Have. The axial center O2 of the rolling wheel 62 is located on the straight line L1.

The wheel damper mechanism 71 has a straight rod-shaped outer shape, and one end side on the rear side is supported by a support flange portion 70, and the rolling wheel 62 is supported on the other end side on the front side. .. The wheel damper mechanism 71 is provided so that the center line of the straight rod shape coincides with the straight line L1 in the side view (see FIG. 6).

The wheel damper mechanism 71 includes a hollow outer cylinder 74 having a hexagonal columnar outer shape and an opening on the front side, and an elastic support shaft 75 having a hexagonal columnar outer shape and movably inserted into the outer cylinder 74. Has. The wheel damper mechanism 71 is configured as a cylinder mechanism that expands and contracts by the axial relative movement of the elastic support shaft 75 with respect to the outer cylinder 74. Inside the wheel damper mechanism 71, a support spring 76, which is an elastic body that elastically supports the elastic support shaft 75 with respect to the outer cylinder 74, is provided.

The elastic support shaft 75 is a tubular member with both ends open, and has a hexagonal cross-sectional insertion structure with respect to the outer cylinder 74 so that the elastic support shaft 75 cannot rotate relative to the outer cylinder 74 and is movable in the axial direction. Has been done. The elastic support shaft 75 exposes the front portion from the outer cylinder 74.

The support spring 76 is a coil spring whose expansion and contraction direction is the axial direction of the wheel damper mechanism 71, and is inserted into the elastic support shaft 75 in the outer cylinder 74 and the rear portion is moved to the rear side from the elastic support shaft 75. It is protruding. The support spring 76 is interposed between the spring receiving plate 77 provided at the rear portion in the outer cylinder 74 and the spring receiving shaft 78 provided at the front portion of the elastic support shaft 75. That is, the support spring 76 is provided in a state where the rear end side is in contact with the spring receiving plate 77 and the front end side is in contact with the spring receiving shaft 78.

The spring receiving plate 77 is a plate-shaped member whose axial direction is the axial direction of the wheel damper mechanism 71, and is fixed to a bolt-shaped adjusting shaft 79 penetrating the rear surface portion 74a forming the rear end surface of the outer cylinder 74. It is provided in a state of being. The adjusting shaft 79 is provided in a state of being screw-engaged with the screw hole 74b of the rear surface portion 74a of the outer cylinder 74, supports the spring receiving plate 77 on the front end side, and is provided at the rear end portion protruding from the rear surface portion 74a. It has a hexagonal operation unit 79a.

By rotating the adjusting shaft 79 by the operating portion 79a, the position of the adjusting shaft 79 in the axial direction with respect to the rear surface portion 74a changes, and the position of the spring receiving plate 77 changes. As a result, the elastic force that the support spring 76 acts on the elastic support shaft 75 is adjusted. The spring receiving shaft 78 is a rod-shaped member having a circular cross-sectional shape, and is fixed to the elastic support shaft 75 in a state of penetrating the elastic support shaft 75 in the left-right direction.

The wheel damper mechanism 71 is provided in a state where the rear portion of the outer cylinder 74 is fixed to the left and right outer surfaces of the support flange portion 70 by welding or the like. On the other hand, a rolling wheel support shaft 80 for supporting the rolling wheel 62 is provided at the tip of the elastic support shaft 75. The rolling wheel support shaft 80 is provided on the front side of the spring receiving shaft 78 in a state of penetrating the tip portion of the elastic support shaft 75 in parallel with the spring receiving shaft 78.

The wheel support shaft 80 extends inward to the left and right from the tip of the elastic support shaft 75, and is inserted into the wheel 62 from the opening 62d opened to the left and right outside in the first wheel portion 62a. The rolling wheel 62 is supported via a bearing or the like provided inside the intermediate shaft portion 62c of the rolling wheel 62. The rolling wheel 62 is rotatably supported with respect to the rolling wheel support shaft 80 about the axis O2. As described above, the wheel 62 is cantilevered with respect to the wheel damper mechanism 71 by the wheel support shaft 80.

In the above configuration, the support flange portion 70 supported by the tubular shaft portion 72 fixed to the drive sprocket 61, the wheel damper mechanism 71, the wheel support shaft 80, and the wheel 62 are centered on the axle center O1. It has a structure that rotates integrally as a sprocket. In the following, an integrated structure including a support flange portion 70, a wheel damper mechanism 71, a wheel support shaft 80, and a wheel 62 will be referred to as a “roll wheel rotation unit”.

The wheel rotation unit is configured to have a line-symmetrical outer shape centered on a straight line L1 passing through the axle center O1 and the axis O2 of the wheel 62 in a side view (see FIG. 6). Therefore, the crawler unit 30 including the wheel rotation unit is configured to have a line-symmetrical outer shape with the straight line L1 as the center.

The crawler 63 is an endless rubber crawler having a predetermined cross-sectional shape on the inner peripheral side and an uneven shape due to lugs formed on the outer peripheral side in a predetermined pattern. The crawler 63 is formed with an engaging hole 63a into which the tooth portion 68 of the drive sprocket 61 is inserted at the central portion in the width direction (see FIG. 5). The drive sprocket 61 is engaged with the crawler 63 by inserting the tooth portion 68 located in the range where the crawler 63 is in contact with the crawler 63 in the circumferential direction into the engaging hole portion 63a.

The crawler 63 has a pair of left and right ridges 63b that are convex inward in a cross-sectional view on the inner peripheral side. The crawler 63 engages with the rolling wheel 62 in a state where the left and right ridges 63b are fitted between the first wheel portion 62a and the second wheel portion 62b with respect to the rolling wheel 62. The drive sprocket 61 is located between the left and right ridges 63b in the left-right direction.

The link 90 will be described. The link 90 is a connecting mechanism composed of a plurality of axial portions, and is a horizontal link portion 91 along the left-right direction and a vertical link portion 92 extending rearward from the left-right outer portion of the horizontal link portion 91. And have. The link 90 is configured to form a substantially "L" shape in a plan view by the horizontal link portion 91 and the vertical link portion 92.

The horizontal link portion 91 has a linear axial inner pipe 93 and a linear axial outer pipe 94 into which the inner pipe 93 is movably inserted in the axial direction. The inner pipe 93 and the outer pipe 94 are provided so that their axes are aligned with each other and the axis directions are aligned in the left-right direction.

The horizontal link portion 91 is provided in a state in which the left and right inner end portions of the inner pipe 93 are supported by the front link support arm 95 provided in a manner fitted to the drive shaft case 36. The front link support arm 95 is composed of a plate-shaped member having a plate thickness direction in the left-right direction, and is provided so as to extend upward from the rear side of a substantially central portion in the axial direction of the drive shaft case 36. There is. The front link support arm 95 supports the inner pipe 93 in a fixed state with the upper left and right inner ends of the inner pipe 93 penetrating the upper end thereof.

The front link support arm 95 is provided in a state of being fixed to the left and right end portions of the rear support frame 96 provided so as to extend to the left and right outward at the rear end portion of the airframe frame 8. The rear support frame 96 supports the rear portion of the mission case 10 from below as a part of the airframe frame 8.

The rear support frame 96 has plate-shaped flange portions 96a having a plate thickness direction in the left-right direction at both left and right ends thereof. The front link support arm 95 is fixed to the rear support frame 96 by a fixing member such as a bolt with its lower portion overlapped with the flange portion 96a. Therefore, as shown in FIGS. 6 and 7, holes 95a for passing the fixing member are formed at two positions in the lower portion of the front link support arm 95. Further, an arc-shaped recess 95b for fitting the drive shaft case 36 from the front side is formed in the lower portion of the front link support arm 95.

As described above, the front link support arm 95 is provided as a portion fixed to the machine body 6 side, and allows the drive shaft case 36 to rotate with the vertical rotation of the chain case 37. The lateral link portion 91 is supported at a fixed position with respect to the machine body 6 side by the front link support arm 95. That is, the position of the axial center P2 of the horizontal link portion 91 is a fixed position with respect to the machine body 6. The horizontal link portion 91 is located above the rear of the drive shaft case 36.

In the horizontal link portion 91, the length of the horizontal link portion 91 is adjusted by the mechanism for adjusting the position of the outer pipe 94 with respect to the inner pipe 93 fixed to the front link support arm 95. The outer pipe 94 is fixed to the inner pipe 93 by a fixing member 97 such as a bolt that radially penetrates the peripheral walls of both pipes. The position adjustment of the outer pipe 94 is used for adjusting the position of the crawler unit 30 in the left-right direction, that is, adjusting the tread of the left and right crawler units 30.

In the vertical link portion 92, the front side is supported by the horizontal link portion 91, and the rear side is supported by the rear link support arm 100 provided in the support flange portion 70, whereby the horizontal link portion 91 and the rear link support arm 100 are supported. It is erected between and. The vertical link portion 92 has a link main body member 101 which forms a majority thereof, and a connecting shaft member 102 for elastically movably connecting and supporting the link main body member 101 with respect to the rear link support arm 100.

The rear link support arm 100 is provided so as to be within the range of the outer shape of the drive sprocket 61 in a side view while being fixed to the support flange portion 70. The rear link support arm 100 has a plate-shaped portion having a plate thickness direction in the left-right direction and a substantially fan shape in a side view, and a shaft support portion 100b provided on the central angle side of the main body portion 100a. Has.

The rear link support arm 100 has a substantially fan-shaped central angle side of the main body portion 100a facing diagonally upward and rearward. In the present embodiment, the side view shape formed by the main body portion 100a is a substantially fan shape having a central angle of about 30 °. A bent surface portion 100c bent to the left and right outward with respect to the main body portion 100a is formed along the upper and lower linear edge portions corresponding to the radius of the substantially fan shape which is the side view shape of the main body portion 100a.

The shaft support portion 100b has a pair of support surface portions 100d facing each other in the left-right direction and a bottom surface portion 100e connected to the main body portion 100a side, and is formed in a substantially "U" shape by these surface portions. A link rear support shaft 105 that supports the rear end portion of the vertical link portion 92 is erected between the pair of left and right support surface portions 100d of the shaft support portion 100b.

The link rear support shaft 105 is an axis whose rotation axis direction is the left-right direction, and is composed of pin-shaped members penetrating the left and right support surface portions of the shaft support portion 100b. A stop pin 105a for locking the shaft is attached to the tip of the link rear support shaft 105 projecting outward from the shaft support portion 100b to the left and right.

The rear link support arm 100 is detachably fixed to the support flange portion 70 by a plurality of bolts 106 (three in this embodiment) which are fixing members penetrating the main body portion 100a and the support flange portion 70. The rear link support arm 100 is fixed by bolts 106 with the substantially fan-shaped arcuate portion of the main body portion 100a overlapped with the trailing edge portion of the support flange portion 70 from the left and right outside.

In the support flange portion 70, five hole portions 70h are formed at predetermined intervals along the arc shape of the trailing edge portion as holes through which the bolt 106 is passed. Further, three holes are formed in the edge portion of the main body portion 100a of the rear link support arm 100 opposite to the shaft support portion 100b side. The three holes of the rear link support arm 100 are formed so as to match the three consecutive holes 70h of the five holes 70h of the support flange 70. Of the five holes 70h, the rear link support arm 100 uses the upper three holes 70h and is fixed to the support flange 70 by three bolts 106.

As shown in FIG. 6, the rear link support arm 100 has a line-symmetrical shape with a predetermined straight line L2 passing through the axis P3 of the link rear support shaft 105 supported by the shaft support portion 100b as a center line in a side view. Have. The axle center O1 is located on the straight line L2.

The link main body member 101 has a pipe-shaped main body shaft portion 111 having a predetermined bending shape, and a support cylinder portion 112 provided on the front end side of the main body shaft portion 111.

The main body shaft portion 111 has a horizontal shaft portion 111a whose central axis direction is the left-right direction from the front side to the rear side, an obtuse shaft portion 111b formed so as to form an obtuse angle together with the horizontal shaft portion 111a, and a front-rear direction in a plan view. It has a vertical axis portion 111c which is an axial portion along the above and has an obtuse angle together with the inclined shaft portion 111b. The main body shaft portion 111 has a shape such that the center lines of the respective shaft portions of the horizontal axis portion 111a, the inclined shaft portion 111b, and the vertical axis portion 111c are located on a common plane, and is linear in a side view. It is supported. In the left-right direction of the main body shaft portion 111, the horizontal shaft portion 111a is positioned within the width range of the crawler 63, and the vertical axis portion 111c is located on the left and right outside of the crawler 63.

The support cylinder portion 112 is a cylindrical portion having both ends opened, and is fixed to the front side of the horizontal shaft portion 111a with respect to the main body shaft portion 111 by welding or the like, with the left-right direction as the central axis direction. The support cylinder portion 112 is provided so as to be movable relative to the outer pipe 94 in a state of penetrating the outer pipe 94. By passing the support cylinder portion 112 through the outer pipe 94 in this way, the front end portion of the link main body member 101, that is, the front end portion of the vertical link portion 92 rotates in the left-right direction with respect to the horizontal link portion 91. It is rotatably supported in the direction of the moving axis.

The horizontal link portion 91 is provided with a stopper member 115 that constitutes a stopper mechanism for restricting the relative movement of the support cylinder portion 112 with respect to the outer pipe 94. As shown in FIG. 8, the stopper member 115 includes a cylindrical or ring-shaped main body cylinder portion 115a having the same diameter or substantially the same diameter as the support cylinder portion 112, and a locking plate extending from the outer peripheral portion of the main body cylinder portion 115a. It has a portion 115b.

As shown in FIG. 8, the stopper member 115 is provided so as to be relatively movable with respect to the outer pipe 94 in a state where the outer pipe 94 is passed through the main body cylinder portion 115a. The locking plate portion 115b is a plate-shaped portion along the radial direction of the main body cylinder portion 115a in the central axial direction of the main body cylinder portion 115a, and is provided in a hanging shape from the lower side of the main body cylinder portion 115a. The locking plate portion 115b extends from the lower side of the main body cylinder portion 115a to the outside in the left-right direction (right side in FIG. 8) which is one side in the central axis direction of the main body cylinder portion 115a.

At the tip of the locking plate portion 115b in the extending direction, a locking portion 115c having a locking surface 115d forming a right angle to the main body portion of the locking plate portion 115b is formed. The locking portion 115c is formed so as to project inward in the radial direction of the main body tubular portion 115a at the tip of the locking plate portion 115b to form a key. The locking portion 115c is formed so as to act only on the support cylinder portion 112 without interfering with the outer pipe 94.

In the stopper member 115, the end surface 115e on the extension side of the locking plate portion 115b of the main body cylinder portion 115a is brought into contact with or substantially in contact with one end surface 112a (left side in FIG. 8) of the support cylinder portion 112. The locking surface 115d is engaged with the support cylinder portion 112 in a state of being in contact with or substantially in contact with the other end surface 112b (on the right side in FIG. 8) of the support cylinder portion 112. That is, the stopper member 115 engages with the support cylinder portion 112 in such a manner that the support cylinder portion 112 is sandwiched between the main body cylinder portion 115a and the locking portion 115c.

In the example shown in FIG. 7 and the like, the stopper member 115 engages with the support cylinder portion 112 on the outer pipe 94 with the main body cylinder portion 115a positioned inward in the left-right direction with respect to the support cylinder portion 112. ing. The stopper member 115 is fixed to the outer pipe 94 by a fixing member 116 such as a bolt penetrating the peripheral wall of the main body cylinder portion 115a and the peripheral wall of the outer pipe 94. In this way, the stopper member 115 is fixed to the outer pipe 94 in a state of being engaged with the support cylinder portion 112, thereby restricting the axial movement of the support cylinder portion 112 on the outer pipe 94.

The connecting shaft member 102 includes a straight rod-shaped main body shaft portion 102a parallel to the vertical axis portion 111c of the main body shaft portion 111, an elastic support cylinder portion 102b provided at the front end portion of the main body shaft portion 102a, and a main body shaft portion 102a. It has a shaft support portion 102c provided on the rear side. The main body shaft portion 102a, the elastic support cylinder portion 102b, and the shaft support portion 102c constitute a connecting shaft member 102 which is an integral member. The connecting shaft member 102 connects the link main body member 101 and the link rear support shaft 105, and supports the link main body member 101 on the link rear support shaft 105.

The elastic support cylinder portion 102b is a cylindrical portion having both ends opened, and is fixed to the left and right sides of the front end portion of the main body shaft portion 102a by welding or the like. The elastic support cylinder portion 102b is provided so as to be movable relative to the reduced diameter portion 111d in a state of penetrating the reduced diameter portion 111d forming the rear portion of the vertical axis portion 111c of the main body shaft portion 111.

In the reduced diameter portion 111d of the main body shaft portion 111, front support springs 117 and rear support springs 118, which are elastic bodies, are provided on the front side and the rear side of the elastic support cylinder portion 102b, respectively. The front support spring 117 and the rear support spring 118 are both wound springs and are provided so as to penetrate the reduced diameter portion 111d.

The front support spring 117 abuts the rear end side on the front end surface of the elastic support cylinder portion 102b, and is engaged by the front locking pin 117a attached to the reduced diameter portion 111d on the front side of the front support spring 117. It has been stopped. The rear support spring 118 has the front end side abutting against the rear end surface of the elastic support cylinder portion 102b, and the rear locking pin 118a attached to the reduced diameter portion 111d on the rear side of the rear support spring 118. It is locked. As described above, the elastic support cylinder portion 102b is elastically supported with respect to the axial movement in a state of being sandwiched by the front and rear springs with respect to the diameter reduction portion 111d.

The shaft support portion 102c is a cylindrical portion whose central axis direction is the left-right direction, and is fixed to the rear end side of the main body shaft portion 102a by welding or the like. The shaft support portion 102c is provided so as to be rotatable relative to the link rear support shaft 105 in a state of penetrating the link rear support shaft 105 erected on the shaft support portion 100b of the rear link support arm 100. As a result, the link main body member 101 is rotatably supported with respect to the post-link support shaft 105.

In this way, in the configuration in which the link main body member 101 is supported with respect to the link rear support shaft 105 via the connecting shaft member 102, the link main body member 101 is elastically supported for axial movement with respect to the connecting shaft member 102. A shock absorber 120 as a damper mechanism is configured. That is, in the shock absorber 120, in the main body shaft portion 111 of the link main body member 101, the elastic support cylinder portion 102b of the connecting shaft member 102 is interposed between the front support spring 117 and the rear support spring 118 to provide the elastic support cylinder portion 102b. It is a mechanism that elastically supports the link main body member 101 with respect to the connecting shaft member 102 by pressing and urging from both sides in the axial direction. The link main body member 101 is elastically supported by the shock absorber 120 in the direction of approaching and separating from the link rear support shaft 105 via the connecting shaft member 102.

In the above configuration, the link 90 constituting the link mechanism 60 is provided parallel to the chain case 37 in a side view. That is, as described above, the link 90 provided so as to be linear in the side view has the direction of the straight line in the side view parallel to or substantially parallel to the longitudinal direction of the chain case 37.

Specifically, as shown in FIG. 6, the straight line along the link 90 in the side view is a straight line R1 passing through the axial center P2 of the horizontal link portion 91 and the axial center P3 of the link rear support shaft 105. The link 90 is symmetrically or substantially symmetrical with respect to the straight line R1. Further, the straight line defining the longitudinal direction of the chain case 37 in the side view is a straight line R2 passing through the axis P1 of the crawler drive shaft 38 and the axle center O1.

In this way, the link 90, together with the chain case 37, constitutes a link mechanism 60 interlocked with the elevating operation of the machine body 6. The link mechanism 60 is a parallel link having four axle centers of the axle center O1, the axis P1 of the drive shaft 38 for the crawler, the axis P2 of the lateral link portion 91, and the axis P3 of the rear support shaft 105 as nodes. In the embodiment, the crawler unit 30 is connected and supported with respect to the machine body 6.

In the link mechanism 60, the axial center P2 of the lateral link portion 91 is located forward and upward with respect to the axle center O1, and the axial center P3 of the link rear support shaft 105 is located rearward and upward with respect to the axle center O1. is doing. In the link mechanism 60, the positions of the axial center P1 of the crawler drive shaft 38 and the axial center P2 of the lateral link portion 91 are fixed positions with respect to the machine body 6 regardless of the raising and lowering operation of the machine body 6. On the other hand, the positions of the axle center O1 and the axle center P3 of the link rear support shaft 105 move as the machine body 6 moves up and down. However, the relative positions of the axle center O1 and the axle center P3 are constant regardless of the elevating operation of the machine body 6.

The transplanting machine 1 provided with the link mechanism 60 as described above operates the link mechanism 60 as shown in FIGS. 1 and 2 as the machine body 6 moves up and down due to the expansion and contraction operation of the elevating cylinder 41. In the operation of the link mechanism 60, the chain case 37 and the link 90 maintain a parallel state in a side view. That is, as shown in FIG. 6, in the side view, the straight line R2 passing through the axle center O1 and the axis P1 of the crawler drive shaft 38, the axis P2 of the lateral link portion 91, and the axis P3 of the link rear support shaft 105. The straight line R1 passing through the link mechanism 60 maintains a state parallel to each other in the operation of the link mechanism 60. Note that FIG. 1 shows a state in which the airframe 6 is raised, and FIG. 2 shows a state in which the airframe 6 is lowered.

Further, the link mechanism 60 includes the axle center O1 which is the axial center position of the axle 39 as a node, and rolls with the rotation operation of the machine body 6 around the axle 39 in a state where the crawler unit 30 is in contact with the ground. The wheel 62 is configured to move up and down. Specifically, it is as follows.

In the state where the crawler unit 30 is grounded, for example, as shown in FIG. 9, the handle 13 is pushed down by the operator who operates the transplanting machine 1 (see arrow B1), so that the transplanting machine 1 touches the grounding of the crawler unit 30. With the portion as a fulcrum, the aircraft 6 is tilted so as to be raised (see arrow B2), and the front wheel 31 is in a floating state. Here, the transplanting machine 1 tilts the machine body 6 backward about the center of the drive sprocket 61 in a state of being grounded via the crawler 63, that is, the axle center O1.

When the machine body 6 tilts backward with respect to the axle center O1, the rear link support arm 100 that supports the link rear support shaft 105 is pushed rearward by the link 90 as the operation of the link mechanism 60 (see arrow B3). .. Since the rear link support arm 100 is fixed to the support flange portion 70 rotatably supported by the cylinder shaft portion 72 with respect to the drive sprocket 61, the rear link support arm 100 is pushed to the rear side. As a result, the wheel rotation unit including the support flange portion 70, the wheel damper mechanism 71, the wheel support shaft 80, and the wheel 62 rotates around the axle center O1, and the wheel 62 rises (see arrow B4). ).

In this way, the link mechanism 60 is configured to separate the rolling wheel 62 from the ground G1 by rotating the machine body 6 about the axle 39 so as to move backward while the crawler unit 30 is in contact with the ground. Has been done.

On the other hand, as shown in FIG. 9, the transplanting machine 1 brings the drive sprocket 61 to the ground via the crawler 63 by relaxing the force for pushing down the handle 13 from the state where the rolling wheels 62 are raised by the backward tilting motion of the machine body 6. The machine body 6 is rotated in the forward tilting direction around the axle center O1 while maintaining the state. As a result, the rolling wheel 62 in a state of being away from the ground G1 will descend.

Further, in the link mechanism 60, the link 90 has a shock absorber 120 in a direction in which the nodes of the link mechanism 60 located at both ends of the link 90 are brought close to each other and separated from each other in a side view. Here, the nodes of the link mechanism 60 located at both ends of the link 90 are the axial center P2 of the horizontal link portion 91 and the axial center P3 of the link rear support shaft 105 (see FIG. 6).

That is, in the vertical link portion 92 of the link 90, the link main body member 101 and the connecting shaft member 102 can move relative to each other in the axial direction due to the through-support structure of the elastic support cylinder portion 102b with respect to the reduced diameter portion 111d of the main body shaft portion 111. It is connected. By providing the front support spring 117 and the rear support spring 118 in front of and behind the elastic support cylinder portion 102b, a shock absorber 120 that elastically supports the relative movement of the link main body member 101 and the connecting shaft member 102 is configured.

By the shock absorber 120, the connecting shaft member 102 moves forward relative to the link main body member 101, so that the shaft center P3 approaches the shaft center P2 with the compression of the front support spring 117. On the other hand, as the connecting shaft member 102 moves rearward relative to the link main body member 101, the shaft center P3 is separated from the shaft center P2 with the compression of the rear support spring 118. In this way, the axis P2 and the axis P3 are close to each other and separated from each other within the range of relative movement between the link main body member 101 and the connecting shaft member 102.

Further, in the examples shown in FIGS. 1 to 9, the left and right crawler units 30 are provided on the left and right outer sides of the chain case 37. The porting machine 1 according to the present embodiment is configured so that the left and right crawler units 30 can be provided on the left and right inside of the chain case 37 without the need for replacement of parts. That is, the porting machine 1 is configured so that the mounting positions of the left and right crawler units 30 can be changed on the left and right outside and inside of the chain case 37 by a common component configuration. In the following, a configuration in which the left and right crawler units 30 are provided on the left and right inside of the chain case 37 is referred to as a “crawler inner arrangement configuration”, and a configuration in which the crawler unit 30 is provided on the left and right outside of the chain case 37 is referred to as a “crawler outer arrangement configuration”. do.

As shown in FIGS. 10 and 11, in the crawler inner arrangement configuration, the crawler unit 30 and the link 90 are provided so as to be symmetrical with respect to the crawler outer arrangement configuration via the chain case 37. FIG. 10 is a plan view showing the configuration of the left half of the suspension in the crawler inner arrangement configuration. FIG. 11 is a side view of the left crawler unit 30 and its surroundings in the crawler inner arrangement configuration as viewed from the inside in the left-right direction.

As for the crawler unit 30, as shown in FIGS. 10 and 11, the crawler unit 30 including the wheel rotation unit is attached to the left and right inside of the chain case 37 in a left-right inverted state. In the crawler inner arrangement configuration, the crawler unit 30 is provided with the side that was left and right outer (lower side in FIG. 5) facing the left and right inner side (upper side in FIG. 10) in the crawler outer arrangement configuration.

Since the crawler unit 30 is configured line-symmetrically with respect to the straight line L1 (see FIG. 6), a configuration in which the crawler unit 30 in the crawler outer arrangement configuration is inverted can be obtained in the crawler inner arrangement configuration. That is, as shown in FIG. 11, the crawler unit 30 in the side view in the crawler inner arrangement configuration is the configuration in which the crawler unit 30 in the side view in the crawler outer arrangement configuration shown in FIG. 6 is inverted left and right in the drawing. Become. When changing the configuration of the crawler outer arrangement configuration and the crawler inner arrangement configuration, the left and right crawler units 30 may be interchanged and attached, and the left or right crawler unit 30 may be inverted on the left or right side, respectively. It may be replaced on the outside or the inside of the chain case 37.

In the crawler inner arrangement configuration, the axle 39 is provided so as to project inward from the rear end of the chain case 37 to the left and right. As shown in FIG. 10, shaft support protrusions 37b and 37c protruding substantially in a columnar shape corresponding to the axle center O1 are provided on both left and right sides of the support portion of the axle 39 at the rear end of the chain case 37. There is.

In the crawler outer arrangement configuration, as shown in FIG. 5, the axle 39 is provided at the rear end portion of the chain case 37 so as to project outward from the left and right outer shaft support protrusions 37b. Here, the end face portions of the left and right inner shaft support protrusions 37c are closed by a circular cap member 119a or the like. On the other hand, in the crawler inner arrangement configuration, as shown in FIG. 10, the axle 39 is provided at the rear end portion of the chain case 37 so as to project inward from the left and right inner shaft support protrusions 37c. .. Here, the end face portions of the left and right outer shaft support protrusions 37b are closed by a circular cap member 119b or the like.

Further, in each of the crawler outer arrangement configuration and the crawler inner arrangement configuration, the rear link support arm 100 uses the upper three hole portions 70h out of the five hole portions 70h formed in the support flange portion 70. It is fixed to the support flange portion 70 by three bolts 106 (see FIGS. 6 and 11). Therefore, for example, when the left and right crawler units 30 are inverted and replaced, if the five hole portions 70h of the support flange portion 70 in the crawler outer arrangement configuration are sequentially set as the first to fifth hole portions 70h from the upper side to the lower side, the crawler In the outer arrangement configuration, the rear link support arm 100 is fixed by using the first, second and third hole portions 70h located on the upper side, and in the crawler inner arrangement configuration, the fifth, fourth and fourth holes located on the upper side are fixed. The rear link support arm 100 is fixed by using the three-hole portion 70h. Since the rear link support arm 100 has a line-symmetrical shape centered on the straight line L2, the rear link support arm 100 is common to the support flange portion 70 in the case of the crawler outer arrangement configuration and the case of the crawler inner arrangement configuration. It becomes the mounting mode of.

As shown in FIGS. 10 and 11, the link 90 is attached in a state where the configuration forming the vertical link portion 92 is horizontally inverted. That is, the vertical link portion 92 is provided so that the vertical axis portion 111c of the main body shaft portion 111 is located on the left and right inside of the crawler 63. Here, a mechanism for adjusting the position of the outer pipe 94 with respect to the inner pipe 93 is used for adjusting the position of the vertical link portion 92 in the left-right direction.

In the crawler inner arrangement configuration, the vertical link portion 92 positions the support cylinder portion 112 on the left and right inside of the stopper member 115 (see FIG. 10). Therefore, the stopper member 115 is inserted into the outer pipe 94 in the opposite direction to the left and right as in the case of the crawler outer arrangement configuration, and engages with the support cylinder portion 112.

Further, the link 90 is configured symmetrically or substantially symmetrically along the straight line R1 (see FIG. 6) in the side view. Therefore, even in the crawler inner arrangement configuration, the link 90 is a straight line passing through the axial center P2 of the lateral link portion 91 and the axial center P3 of the link rear support shaft 105 in the side view as in the case of the crawler outer arrangement configuration. It will be in line with it.

As described above, in the transplanting machine 1, the left and right crawler units 30 can be replaced on the outside or the inside of the chain case 37. In addition, according to the change of the tread of the left and right crawler units 30 due to the replacement of the crawler unit 30, the positions of the left and right front wheels 31 in the left and right directions are aligned with the positions of the crawler units 30, respectively. The tread is adjusted.

According to the transplanting machine 1 according to the present embodiment having the above-mentioned configuration, good turning performance can be obtained in a configuration having a crawler unit 30 for moving the machine body 6.

The transplanting machine 1 according to the present embodiment constitutes a link mechanism 60, which is a parallel link that operates as the machine body 6 moves up and down, by means of a chain case 37 and a link 90. Then, the link mechanism 60 includes the position of the axle center O1 as a node, and moves the wheel 62 up and down with the rotational operation of the machine body 6 about the axle 39 in a state where the crawler unit 30 is in contact with the ground. It is configured in.

According to such a configuration, it is possible to maintain the parallel state of the machine body 6 and the crawler unit 30 with respect to the rotation of the transplanting machine 1 around the axle center O1. As a result, the rolling wheel 62 side can be raised while maintaining the ground contact state of the crawler unit 30 with the backward tilting rotation of the machine body 6 about the axle center O1. That is, instead of grounding the entire portion of the crawler 63 on the ground contact surface side from the lower portion of the drive sprocket 61 to the lower side of the rolling wheel 62, the rolling wheel 62 side is floated to lift the driving sprocket 61 of the crawler 63. Only the lower part can be grounded. As a result, the machine body 6 can be easily turned and the small turning property can be ensured.

In particular, in the transplanting machine 1 of the present embodiment, the rolling wheels 62 are arranged in front of the drive sprocket 61, and the traveling machine body 2 is rotated backward to minimize the contact area of the crawler unit 30. be able to. That is, when the transplanting machine 1 is turned, the traveling machine 2 is rotated so as to move backward so that the front wheels 31 are floated. Here, the link mechanism 60 is used to rotate the traveling machine 2 so that the traveling machine 2 is in a floating state. The crawler unit 30 also tilts forward in conjunction with the rotation. Therefore, since the portion of the crawler unit 30 on the rolling wheel 62 side can be floated together with the front wheel 31, the ground contact area of the crawler unit 30 can be minimized. This makes it possible to easily turn.

Specifically, for example, as shown in FIG. 9, by pushing down the handle 13 to bring the machine body 6 into a backward tilted state, the front wheels 31 are in a floating state, and the crawler unit 30 raises the rolling wheels 62. Only the portion of the drive sprocket 61 is grounded via the crawler 63. That is, the crawler unit 30 is in a state of line contact with the ground G1. As a result, the ground contact surface can be the same as in the case of the wheel type configuration in which the wheels are connected instead of the crawler unit 30, so that the ground contact area can be reduced and good turning performance can be obtained.

Further, during normal traveling of the transplanting machine 1, the link mechanism 60 can maintain the ground contact state of the crawler unit 30 by the drive sprocket 61 and the rolling wheels 62. This makes it possible to sufficiently obtain the effect of reducing the ground pressure in the case of the foil type configuration.

Further, by configuring the link mechanism 60 with the chain case 37 and the link 90, the ground contact angle of the crawler unit 30 can be kept constant regardless of the height position of the machine body 6. As a result, the traction force of the traveling unit 7 can be stabilized.

Further, the link 90 constituting the link mechanism 60 has a shock absorber 120. According to such a configuration, with respect to the rotation around the axle center O1 of the transplanting machine 1, the link main body member 101 by the shock absorber 120 is based on the state where the machine body 6 and the crawler unit 30 are maintained in a parallel state. Within the range of relative movement of the connecting shaft member 102, relative rotation of the crawler unit 30 about the axle center O1 with respect to the machine body 6 can be allowed. As a result, the crawler unit 30 can be rotated with respect to the machine body 6 in accordance with the unevenness of the road surface in the field, and the pitching of the machine body 6 can be suppressed. That is, for example, in the case of a configuration without the shock absorber 120, since the horizontal state of the crawler unit 30 with respect to the machine body 6 is maintained, the entire body 6 is easily pitched due to the unevenness of the road surface in the field, but the link 90 is a shock absorber. By having 120, such pitching will be suppressed.

Further, the link 90 has a stopper member 115 for adjustably supporting the position of the vertical link portion 92 in the left-right direction in the horizontal link portion 91 and fixing the support position of the vertical link portion 92. According to such a configuration, the treads of the left and right crawler units 30 can be adjusted according to the ridge width and the like in the field.

Further, the porting machine 1 according to the present embodiment adopts a symmetrical configuration for the crawler unit 30 and the link 90, so that the crawler unit 30 has an inner / outer mounting position with respect to the chain case 37 due to a common component configuration. It is possible to change. According to such a configuration, the tread adjustment range of the left and right crawler units 30 can be widened, so that the versatility of the transplanting machine 1 can be improved with respect to the ridge width and the like in the field. Further, regarding the replacement of the crawler unit 30, it is possible to facilitate the management of parts and prevent mistakes in mounting the parts.

[About the configuration of the crawler unit]
Another embodiment of the crawler unit 30 as a crawler traveling device will be described. The present embodiment is for a drive sprocket 61 as a drive wheel included in the crawler unit 30.

For example, when the crawler unit 30 is locked by biting a stone or the like between the drive sprocket 61 and the wheel 62 when the transplanting machine 1 is moving forward, the support flange portion 70 and the wheel damper with respect to the drive sprocket 61. The rolling wheels 62 connected via the mechanism 71 tend to rotate downward about the axle center O1. In such a case, an excessive torque acts on the axle 39 and the like due to the reaction force received by the rolling wheel 62 from the ground G1, and there is a possibility that defects such as deformation and breakage may occur in the parts constituting the traveling drive system.

The following techniques are known for the sprockets constituting the crawler traveling device. As a first prior art, for example, in Japanese Patent Publication No. 48-000247, the tooth portion of the sprocket is composed of a plurality of parts that can be attached to and detached from the boss, and the parts can be replaced when the teeth are worn. Possible so-called segment type sprockets are listed. Further, as a second prior art, Japanese Patent Application Laid-Open No. 2012-056578 describes an inner ring body attached to a mounting portion on the axle side and an inner ring in order to enable tread change within a more appropriate range with a simple structure. Disclosed is a sprocket comprising an outer ring body attached to the body and an outer peripheral engaging ring attached to the outer ring body and having teeth that engage the crawler.

Further, as a third prior art, Japanese Patent Publication No. 56-05020 describes a tooth profile that can be replaced in a concave groove formed in a peripheral portion of a sprocket body as a portion that comes into contact with a roller in a sprocket in a chain transmission device. The configuration with the blocks attached is disclosed.

According to the above-mentioned conventional technique, it is difficult to drive the crawler traveling device with the replaceable parts constituting the tooth portion of the sprocket removed. Therefore, it is not possible to adjust the transmission torque to function as a torque limiter by changing the number of teeth of the sprocket. Further, in the case of the first conventional technique and the second conventional technique, as the replacement of parts due to tooth wear or the like, it is necessary to replace each segment having a plurality of teeth.

Therefore, the crawler unit 30 according to the present embodiment has realized a configuration in which the torque transmitted from the drive sprocket 61 to the crawler 63 and the like can be changed, and good maintainability can be obtained.

As shown in FIGS. 12 and 13, the crawler unit 30 according to the present embodiment includes a drive sprocket 61 that transmits propulsive force to the crawler 63. The drive sprocket 61 includes a rim portion 137 which is an outer peripheral portion along the circumference centered on the central axis Q1 corresponding to the axle center O1, and a plurality of drive sprocket 61s which project radially outward from the rim portion 137 and transmit propulsive force to the crawler 63. It is provided with a tooth portion 138 as a protruding portion of the wheel. A part of the tooth portions 138 out of the plurality of tooth portions 138 is detachably configured.

The drive sprocket 61 has a sprocket body 130 and a plurality of tooth mounting members 140 that are detachably provided with respect to the sprocket body 130.

The sprocket main body 130 is a member forming the main body portion of the drive sprocket 61, and has a substantially disk shape centered on the central axis Q1. The sprocket body 130 includes a substantially disk-shaped hub portion 135 that forms a central portion thereof and receives an axle 39 connected to the sprocket body 130, and a plurality of spoke portions 136 formed radially from the hub portion 135 around the central axis Q1 and a sprocket. It has a rim portion 137 forming a peripheral edge portion of the main body 130.

A plurality of tooth portions 138 serving as engagement portions with the crawler 63 are provided on the outer peripheral side of the rim portion 137 at predetermined intervals in the circumferential direction. The tooth portion 138 is formed so as to form a mountain shape toward the outside in the radial direction in the central axial direction of the drive sprocket 61.

The spoke portion 136 is a narrow portion that connects the outer peripheral side of the hub portion 135 and the inner peripheral side of the rim portion 137. In this embodiment, six spoke portions 136 are formed at equal intervals in the circumferential direction. Therefore, between the hub portion 135 and the rim portion 137, an opening 139 is formed between two spoke portions 136 adjacent to each other in the circumferential direction. The openings 139 are formed at six locations at equal intervals in the circumferential direction.

As shown in FIGS. 12 to 14, the tooth mounting member 140 supports and fixes the tooth forming plate portion 141 including the protrusion 148 forming the tooth portion 138 of the drive sprocket 61 and the tooth forming plate portion 141 to the sprocket body 130. It has a support fixing plate portion 142 for the purpose. The tooth forming plate portion 141 and the support fixing plate portion 142 form a tooth mounting member 140 as an integral attachment / detachment member to the sprocket body 130 by fixing the plate-shaped members forming the respective plates to each other by welding or the like. There is. The plate thickness of each of the tooth forming plate portion 141 and the support fixing plate portion 142 is the same as or substantially the same as the plate thickness of the sprocket body 130.

The tooth forming plate portion 141 has a main body portion 143 which is a substantially rectangular plate-shaped portion, and a protruding portion 148 is formed so as to protrude from one side of the main body portion 143. The protrusion 148 is formed in the center of the side portion 143a on one side of the main body 143, and the tooth forming plate portion 141 has a line-symmetrical shape centered on the straight line T1 that divides the protrusion 148 into left and right. (See FIG. 12). The straight line T1 is a straight line parallel to the side portion 143c orthogonal to the side portion 143a on the side opposite to the side portion 143a on the side where the protrusion portion 148 protrudes in the main body portion 143. The side portion 143a on the side where the protrusion 148 of the main body 143 protrudes has a shape along an arc having the same or substantially the same curvature as the arc along which the outer edge of the rim portion 137 of the sprocket main body 130 protrudes.

The support fixing plate portion 142 is an elongated rectangular plate-shaped portion, and is provided on one plate surface side of the plate-shaped member forming the tooth forming plate portion 141. The support fixing plate portion 142 is provided so as to follow the longitudinal direction along the side portion 143b of the main body portion 143 with respect to the tooth forming plate portion 141.

The support fixing plate portion 142 is provided so as to overlap the entire width direction with the tooth forming plate portion 141. The support and fixing plate portion 142 has both sides in the longitudinal direction as an extension portion 142a extending outward from the left and right side portions 143c of the main body portion 143 of the tooth forming plate portion 141. The support fixing plate portion 142 is provided so that the tooth mounting member 140 has a line-symmetrical shape with respect to the tooth forming plate portion 141 as a whole with the straight line T1 as the center.

In the sprocket main body 130, in order to attach the tooth attachment member 140, a notch 133 is formed by cutting out a forming portion of one tooth portion 138 and a portion in the vicinity thereof in the circumferential direction of the rim portion 137. The cutout portion 133 is formed so as to be connected to the opening portion 139 by the end portions 137a of the rim portion 137 facing each other. That is, in the sprocket main body 130, of the plurality of openings 139, the opening 139A connected to the opening 139 is opened to the outer peripheral side by the notch 133. The rim portion 137 is formed intermittently in the circumferential direction by the notch portion 133.

A tooth mounting member 140 is provided for the opening 139A in which the notch 133 is formed. In the present embodiment, of the six openings 139, notches 133 are formed with respect to the three openings 139A that are alternately located in the circumferential direction of the sprocket body 130. That is, a maximum of three tooth attachment members 140 can be attached to the sprocket body 130.

The tooth attachment member 140 is attached to the sprocket main body 130 in a state where a portion near the protrusion 148 of the main body portion 143 is located in the notch portion 133 and most of the main body portion 143 is located in the opening portion 139A. The tooth mounting member 140 is mounted on the sprocket body 130 in a state where the support fixing plate portion 142 is erected between the two spoke portions 136 that are adjacent to each other in the circumferential direction and form the opening 139A.

The tooth mounting member 140 is detachably fastened and fixed to the sprocket body 130 by the extension portion 142a of the support fixing plate portion 142, the bolt 151 penetrating the sprocket body 130, and the nut 152 that receives the screw of the bolt 151. Therefore, holes 142b for passing the bolt 151 are formed at both ends of the support fixing plate portion 142, and the bolt 151 is passed through the vicinity of the rim portion 137 of the spoke portion 136 of the sprocket body 130. A hole 136a for the purpose is formed (see FIG. 13). The bolt 151 and the nut 152 are examples of fixing members for fixing the tooth mounting member 140 to the sprocket body 130, and other fixing means may be used.

The tooth mounting member 140 closes the notch 133 by the side portion 143a side portion of the main body portion 143 in a state of being mounted on the sprocket main body 130 (hereinafter referred to as “mounting state”). That is, the dimension in the width direction of the main body portion 143 is substantially the same as the dimension between the edge portions 137a forming the notch portion 133, and the main body portion 143 is fitted in the notch portion 133. Further, the tooth mounting member 140 has the side portion 143a along an arc shape along which the outer edge of the rim portion 137 of the sprocket body 130 follows. Further, in the mounted state, the tooth mounting member 140 has plate surfaces on both sides of the tooth forming plate portion 141 flush with respect to the plate surfaces on both sides of the sprocket body 130, respectively.

In the mounted state of the tooth mounting member 140, the protrusion 148 becomes the tooth portion 138 of the drive sprocket 61. In this embodiment, the drive sprocket 61 has 18 teeth 138. Of the 18 tooth portions 138, a maximum of three tooth portions 138 are formed by the protrusions 148 of the tooth mounting member 140. Therefore, five tooth portions 138 are formed between the notches 133 adjacent to each other in the circumferential direction of the sprocket body 130.

In the above configuration, the number of tooth portions 138 is 16 when only one tooth attachment member 140 is attached, and the number of tooth portions 138 is 17 when only two tooth attachment members 140 are attached. In the state where all three tooth attachment members 140 are attached, the number of tooth portions 138 is 18. The drive sprocket 61 in any state functions as a drive wheel of the crawler unit 30.

Further, as shown in FIG. 12, in a state where the three tooth attachment members 140 are attached, the drive sprocket 61 is basically 13 consecutive drive sprockets other than the 5 consecutive tooth portions 138A located on the rolling wheel 62 side. The tooth portion 138 is engaged with the crawler 63. Therefore, by removing one tooth mounting member 140, the minimum number of tooth portions 138 that engage with the crawler 63 becomes twelve. Further, by removing the two tooth mounting members 140, the minimum number of tooth portions 138 that engage with the crawler 63 becomes 11. Further, by removing the three tooth mounting members 140, the minimum number of tooth portions 138 that engage with the crawler 63 becomes 10.

According to the crawler unit 30 according to the present embodiment having the above configuration, the torque transmitted from the drive sprocket 61 to the crawler 63 and the like can be adjusted by the number of tooth mounting members 140 attached to the sprocket body 130. can. This makes it possible to make the engaging portion of the drive sprocket 61 with respect to the crawler 63 function as a torque limiter.

Therefore, for example, in a field with a relatively large amount of stones, stones or the like are caught between the drive sprocket 61 and the rolling wheels 62 in the crawler unit 30, or between the crawler 63 and the driving sprocket 61 and the rolling wheels 62, respectively. In a situation where stone biting is likely to occur, for example, when the drive sprocket 61 has a large diameter and the amount of engagement with the crawler 63 is large (the engagement range in the circumferential direction is large), the drive sprocket 61 can transmit to the crawler 63 and the like. The torque becomes excessive.

Therefore, the transmission torque from the drive sprocket 61 can be reduced by removing an appropriate number of tooth mounting members 140 to reduce the number of tooth portions 138. As a result, the driving force of the crawler 63 by the driving sprocket 61 can be reduced, and the crawler 63 can function as a torque limiter.

That is, when the torque becomes a certain magnitude or more, the drive sprocket 61 can be idled with respect to the crawler 63, and it is possible to prevent an excessive torque from acting on the axle 39 and the like. This makes it possible to prevent defects such as deformation and breakage of the parts constituting the traveling drive system from occurring. Moreover, since it is not necessary to provide a limiter in the traveling drive system, the structure can be simplified. When reducing the transmission torque from the drive sprocket 61, it is preferable to remove all three tooth mounting members 140 in order to make the notch 133 at equal intervals in the circumferential direction of the drive sprocket 61.

Further, when the tooth portion 138 is deteriorated or damaged due to long-term use of the crawler unit 30, only the tooth portion 138 can be replaced instead of the entire drive sprocket 61. In particular, since the tooth attachment member 140 has one protrusion 148 that becomes the tooth portion 138, only one tooth portion 138 can be replaced. Thereby, good maintainability and economy can be obtained.

In the present embodiment, the drive sprocket 61 has a configuration in which three tooth attachment members 140 can be attached, but the number of tooth attachment members 140 that can be attached depends on the total number of tooth portions 138 of the drive sprocket 61 and the like. It is determined as appropriate and is not limited. The number of tooth mounting members 140 that can be mounted may be one, two, or four or more.

Further, regarding the protrusion 148 of the tooth mounting member 140, at least one of the protrusion amount and the protrusion shape is related to the tooth portion 138 provided on the sprocket body 130, or the protrusion portion of the other tooth mounting member 140. It may be different in relation to 148.

Here, the protrusion amount of the protrusion 148 is the protrusion dimension of the protrusion 148 from the side portion 143a, and is the protrusion dimension U1 in the radial direction from the circumference along which the side portion 143a is along (see FIG. 13). Further, the protruding shape of the protruding portion 148 may be, for example, a trapezoidal shape or a rectangular shape.

In this way, by changing the protrusion amount and the protrusion shape of the protrusion 148 that becomes the tooth portion 138, the transmission torque from the drive sprocket 61 can be finely adjusted. This makes it possible to realize appropriate torque transmission according to the working environment such as field conditions.

(Modification example)
A modified example of the drive sprocket 61 will be described with reference to FIG. In this modification, the drive sprocket 61 has a plurality of tooth members 160 as members that are detachably provided with respect to the sprocket body 130 and form the tooth portions 138.

The tooth member 160 has a main body tooth portion 168 forming a tooth portion 138 of the drive sprocket 61, and a mounting plate portion 161 for attaching the tooth member 160 to the sprocket main body 130. The mounting plate portion 161 is a portion in which the base side of the mountain shape of the main body tooth portion 168 is extended into a rectangular shape or a trapezoidal shape. The tooth member 160 is an integral plate-shaped member having the same or substantially the same plate thickness as the plate thickness of the sprocket body 130.

In the tooth member 160, the mounting plate portion 161 is superposed on the plate surface on one side of the rim portion 137 of the sprocket body 130, and the bolts 163 and the bolts 163 that penetrate the mounting plate portion 161 and the rim portion 137 are screwed together. It is detachably fastened and fixed to the sprocket body 130 by a receiving nut (not shown). Therefore, a hole 161a for penetrating the bolt 163 is formed in the central portion of the mounting plate portion 161, and a hole portion for penetrating the bolt 163 in a predetermined portion of the rim portion 137 of the sprocket body 130. 137b is formed. The bolt 163 and the nut are examples of fixing members for fixing the tooth member 160 to the sprocket body 130, and other fixing means may be used. Further, in this modification, the notch portion 133 is not formed in the rim portion 137, and the rim portion 137 is formed so as to be continuous in a circumferential shape over the entire circumference.

In the mounted state of the tooth member 160, the main body tooth portion 168 becomes the tooth portion 138 of the drive sprocket 61. In this modification, a maximum of 6 tooth members 160 can be attached, and of the 18 tooth portions 138, a maximum of 6 tooth portions 138 are formed by the main body tooth portions 168 of the tooth member 160. Tooth. The attachment portions of the tooth member 160 are provided at equal intervals in the circumferential direction of the drive sprocket 61. Therefore, two tooth portions 138 are formed between the attachment portions of the tooth members 160 adjacent to each other in the circumferential direction of the sprocket body 130.

In the above configuration, by removing all the tooth members 160 from the sprocket body 130, the number of tooth portions 138 becomes 12. By reducing the number of tooth members 160 attached to the sprocket body 130 to one, the number of tooth portions 138 becomes thirteen. Similarly, by setting the number of tooth members 160 attached to the sprocket body 130 to 2 to 6, the number of tooth portions 138 is 14 to 18, respectively. The drive sprocket 61 in any state functions as a drive wheel of the crawler unit 30.

Further, in the state where the six tooth members 160 are attached, the drive sprocket 61 basically has 13 consecutive teeth other than the five continuous tooth portions 138A (see FIG. 12) located on the rolling wheel 62 side. The portion 138 is engaged with the crawler 63. Therefore, by removing the 1 to 4 tooth members 160, the minimum number of tooth portions 138 engaged with the crawler 63 is 12 to 9, respectively. Further, by removing the five or six tooth members 160, the minimum number of tooth portions 138 that engage with the crawler 63 becomes eight.

Even with the crawler unit 30 provided with the drive sprocket 61 of the above-mentioned modification, the transmission torque from the drive sprocket 61 can be adjusted by the number of the tooth members 160 attached to the sprocket body 130. This makes it possible to make the engaging portion of the drive sprocket 61 with respect to the crawler 63 function as a torque limiter. When reducing the transmission torque from the drive sprocket 61, it is preferable to remove the tooth members 160 so that the portions from which the tooth members 160 are removed are evenly spaced in the circumferential direction of the drive sprocket 61.

Further, according to the tooth member 160, since only one tooth portion 138 can be replaced, good maintainability and economy can be obtained. In the present embodiment, the drive sprocket 61 has a configuration in which three tooth members 160 can be attached, but the number of attachable tooth members 160 is appropriately determined depending on the total number of tooth portions 138 of the drive sprocket 61 and the like. It is possible, not limited. In the configuration of the modification, all of the 18 tooth portions 138 of the drive sprocket 61 may be formed by the main body tooth portions 168 of the tooth member 160. Further, as in the case of the tooth mounting member 140, at least one of the protrusion amount and the protrusion shape of the main body tooth portion 168 is related to the tooth portion 138 provided on the sprocket main body 130, or the main body of the other tooth member 160. It may be different in relation to the tooth portion 168.

The description of the above-described embodiment is an example of the present invention, and the walking type working machine according to the present invention is not limited to the above-mentioned embodiment. Therefore, it goes without saying that various changes can be made according to the design and the like as long as the technical idea does not deviate from the technical idea of the present invention, even if the embodiment is other than the above-described embodiment. In addition, the configurations of the above-described embodiments can be combined as appropriate.

In the above-described embodiment, the transplanting machine 1 includes a chain case 37 containing a chain transmission mechanism as an example of a transmission case, but the transmission case according to the present invention has another transmission mechanism including, for example, a belt and a pulley. It may be configured.

1 Porting machine 2 Traveling machine 6 Machine 30 Crawler unit 37 Chain case (transmission case)
39 Axles 60 Link mechanism 61 Drive sprocket (driving wheels)
62 Rolling wheel (driving wheel)
63 Crawler 90 Link 91 Horizontal link part 92 Vertical link part 120 Cushioning device 130 Sprocket body 135 Hub part 136 Spoke part 137 Rim part 138 Tooth part 140 Tooth mounting member 141 Tooth forming plate part 142 Support fixing plate part 148 Protrusion part 160 Tooth member 168 Main body tooth part G1 Ground O1 Axle center P2 Axle center P3 Axle center

Claims (3)

It is a walking type work machine that can be moved by a walking worker.
A crawler unit for moving the aircraft,
A transmission case supported by the aircraft and
Along with the transmission case, a link constituting a link mechanism interlocked with the raising and lowering operation of the aircraft is provided.
The crawler unit has a drive wheel supported by an axle provided in the transmission case, a driven wheel, and a crawler wound around the drive wheel and the driven wheel.
The link mechanism includes the axial center position of the axle as a node, and is configured to move the driven wheel up and down with the rotational operation of the machine around the axle in a state where the crawler unit is in contact with the ground. A walking type work machine characterized by being used. The driven wheel is arranged in front of the driving wheel.
The link mechanism is characterized in that the driven wheel is separated from the ground by rotating the airframe about the axle so as to move backward while the crawler unit is in contact with the ground. The walking type work machine according to claim 1. The walking type work according to claim 1 or 2, wherein the link has a shock absorber in a direction in which the nodes of the link mechanism located at both ends of the link are brought close to each other and separated from each other in a side view. Machine.

Images