JP2019076009A - Combine harvester - Google Patents

Abstract

To solve a problem of jamming of grain culms in a transportation device by allowing an operation of a transportation unit in an opposite direction with a simple structure without causing complication of a structure.SOLUTION: A combine harvester includes a reaping unit for reaping grain culms, and a transportation unit for transporting the grain culms reaped by the reaping unit to a threshing unit. The transportation unit includes a transportation mechanism for transporting the grain culms reaped by rotation in one direction to the threshing unit, a rotation restriction unit which restricts the rotation in the one direction of the transport mechanism and makes the transportation mechanism to a restricted state, and a checking unit 500 which checks the transportation mechanism from becoming the restricted state until a prescribed condition is satisfied. In the restricted state by the restriction unit, the rotation mechanism is configured to be rotatable in a direction opposite to the one direction.SELECTED DRAWING: Figure 18

Description

  [0001] The present invention relates to a combine equipped with a transport unit that transports a grain crucible cut by a reaper to a threshing unit.

  Conventionally, there is a combine equipped with a feeder as a conveyance part which conveys to the threshing part the cereal grain which was cut off by the mowing part. The feeder has a configuration in which a conveyor for transporting cereals is provided in a feeder house as a housing. The conveyor has a reaper input shaft axially oriented in the left-right direction as a drive shaft of the conveyor pivotally supporting its feed end side.

  The rear end portion of the feeder is rotatably supported on the traveling machine side of the combine, with the reaper input shaft as a rotation axis. The feeder constitutes a reaper together with a cutting blade device and a take-up reel provided on the front side thereof, and the reaper is configured to move up and down by the rotation of the feeder relative to the traveling machine body.

  Among such combine harvesters, there are some combine harvesters provided with a configuration for reversing the conveyor in order to clear the jammed cereals in case the cereal grits are clogged by the feeder (for example, Patent Document 1, 2)).

  Patent Document 1 discloses a configuration in which reverse rotation power extracted from a threshing cylinder transmission for transmitting engine power to a threshing barrel is transmitted to a reaper input shaft serving as a conveyor input shaft of a feeder through a reverse clutch. It is disclosed. In such a configuration, the feeder is driven to rotate in the reverse direction by turning on the reverse clutch, for example, when clogging of cereal grains occurs in the feeder.

  Further, in Patent Document 2, a reversing mechanism for reversing the rotation transmitted to the reaper input shaft serving as a conveyor input shaft of a feeder, a threshing cylinder input shaft for receiving a power of the engine and rotating a threshing drum of a threshing part and a reaper input Disclosed is a configuration provided with a transmission mechanism between the shaft and a reverse rotation mechanism in which an input / output clutch for reverse rotation power to the reaper input shaft is provided. The reversing mechanism of Patent Document 2 is composed of a pulley, a belt and a gear for transmitting power for reversing the repelling input shaft, and a shaft for supporting these.

JP 2014-14333 A JP, 2016-136924, A

  All of the conventional techniques as described above have a configuration in which a transmission mechanism for reverse rotation for reversing the conveyor is provided in a path for transmitting power from the engine to the reaper. For this reason, the power transmission mechanism from the engine to the reaper is structurally complicated, the number of parts is increased, and the cost is disadvantageous. Further, as in the configuration of Patent Document 2, according to the configuration in which the power transmission mechanism for reverse rotation is branched from the power transmission path for forward rotation of the reaper input shaft, the power transmission mechanism for forward / reverse rotation is A structure is needed to avoid mutual interference. For this reason, there is a problem that the structure becomes complicated or the device configuration becomes large.

  In view of this situation, the main object of the present invention is to enable the operation of the transport unit in the reverse direction with a simple structure without complicating the structure, and to eliminate the clogging of cereal grains in the transport device It is in the point of providing the combine that can be done.

According to a first aspect of the present invention, there is provided a reaping section for reaping a grain scale,
And a transport unit that transports the grain remnants harvested by the reaper to the threshing unit,
The transport unit transports the grain scraps cut by rotation in one direction to the threshing part, and restricts rotation in one direction by the transport mechanism to turn the transport mechanism into a restricted state. The control unit includes: a control unit; and a check control unit that controls the transfer mechanism from being in a control state until a predetermined condition is established.
The conveyance mechanism is configured to be rotatable in a direction opposite to the one direction in a restriction state by the rotation restriction portion.

  According to this configuration, the transport mechanism can be rotated in the opposite direction to the one direction only by being restricted by the rotation regulation portion, so that the transport mechanism can be simplified by a simple structure without causing complication of the structure. Can be rotated in the opposite direction to one direction. This makes it possible to eliminate the clogging of cereal grains in the transport device.

  When the transport mechanism is in the regulation state, the rotation regulating portion regulates rotation in one direction by the transport mechanism. At this time, if the rotation in one direction in the conveyance mechanism is continued, the rotation restriction portion forcibly restricts the rotation in one direction, and a large force is applied to the rotation restriction portion and the conveyance mechanism. The rotation restricting portion, the transport mechanism, and the like may be easily damaged.

  Therefore, according to the present configuration, the check control unit is provided to check that the transfer mechanism is in the restricted state until a predetermined condition is satisfied. Thus, until the predetermined condition is satisfied, the rotation restricting portion does not restrict rotation of the transfer mechanism in one direction by the check of the check portion, and a large force is applied to the rotation restricting portion and the transfer mechanism. It can be suppressed. At this time, by setting the predetermined condition as a condition in which the rotation in one direction in the transport mechanism is stopped when the condition is satisfied, the rotation restriction unit is stopped after the rotation in one direction in the transport mechanism is stopped. Thus, the rotation of the transport mechanism in one direction can be restricted, and damage to the rotation restricting portion, the transport mechanism, and the like can be effectively suppressed.

According to a second aspect of the present invention, there is provided an airframe including the reaper, the transport portion, and the threshing portion;
And a movement control unit for restricting the movement of the machine body by being activated.
The predetermined condition includes the fact that the machine movement control unit is in an operating state.

  According to this configuration, the machine movement restricting unit is activated to restrict movement of the machine, so that the predetermined condition is satisfied, and the rotation restricting unit restricts rotation in one direction in the transport mechanism. Thus, the transport mechanism can be put in a restricted state. Thus, a sufficient time for stopping the rotation in one direction in the transport mechanism can be secured, and damage to the rotation restricting portion, the transport mechanism, and the like can be suppressed. Moreover, in a state in which the movement of the machine is restricted by the machine movement regulating unit, the conveyance mechanism can be rotated in the direction opposite to the one direction to perform the work of eliminating the clogging of the grain scale in the conveyance device. It is possible to carry out the work of eliminating the clogging of the coffin efficiently.

  A third characterizing feature of the present invention is that the machine body movement regulating unit is configured so as not to be able to switch from the actuated state to the non-actuated state when the transport mechanism is regulated by the rotation regulating portion. is there.

  According to this configuration, in the state in which the conveyance mechanism is in the restriction state by the rotation restriction portion, the machine movement restriction portion can not be switched from the operation state to the non-operation state. While rotating, it is possible to avoid a state in which the machine moves, and to prevent the movement of the machine not intended by the operator, etc. It is possible to do the work of clearing the clogging of the grain cans efficiently.

According to a fourth aspect of the present invention, there is provided a work operation tool for operating the reaper and the transport unit.
As an operation position of the work operation tool, the operation operation position for operating the reaper in an operating state and rotating the transport mechanism in the one direction, and setting the reaper in a non-operating state to the one direction in the transport mechanism Reverse operation for stopping the rotational drive of the motor and for stopping the transport mechanism in the opposite direction to the one direction by setting the transport mechanism in the control state by setting the cutting mechanism in the non-operating state and the rotation control portion Including position and
The check control unit is configured to be able to check that the transport mechanism is in the restricted state by checking the movement of the work operation tool to the reverse operation position until the predetermined condition is satisfied.

  According to this configuration, by using the operation operation tool for operating the reaper and the conveyance unit, the conveyance operation mechanism is controlled by the rotation restricting unit by operating the operation operation tool to the reverse operation position. It can be rotatable in the opposite direction to the direction. Thus, the operability can be improved for making the transport mechanism rotatable in the direction opposite to the one direction while simplifying the configuration. Moreover, since the check control unit checks the movement of the operation operation tool to the reverse operation position to check that the transport mechanism is in the restricted state, the check control by the check control unit is also suitable while simplifying the configuration. Can be done. Incidentally, the work operation tool can be a work operation tool that operates the connection and disconnection of the power with respect to the reaper portion and the conveyance portion.

According to a fifth aspect of the present invention, there is provided an airframe including the reaper, the transport portion, and the threshing portion;
An airframe movement restricting portion which restricts the movement of the airframe by being activated;
An aircraft movement regulation operating tool for operating the aircraft movement regulation unit;
The operation position of the machine movement restricting operation tool includes a non-operating position where the machine movement restricting portion is inactivated, and an operation position where the machine movement restricting portion is activated.
The check control unit is movable in conjunction with the movement of the machine movement restricting operation tool, and when the machine movement restricting operation tool is positioned at the inoperative position, the transport mechanism is in the restriction state. There is a point in which it is switched to a check-control state in which a check-control is performed, and it is switched to a check-release state in which the check-control state is released as the predetermined condition is satisfied.

  According to this configuration, the check control unit can move in conjunction with the movement of the machine movement restriction operating tool, so that the movement is controlled while effectively simplifying the structure while effectively utilizing the movement of the machine movement restriction control tool. It is possible to properly switch between the state and the release state. In addition, when the machine movement restricting operation tool is positioned at the inoperative position and the machine movement restricting portion is inactivated, the check portion can be appropriately switched to the check state, and the operation position of the machine movement restricting operation tool If the predetermined condition is satisfied in accordance with the movement to the lower side, the check control unit can be appropriately switched to the check release state when the machine movement control unit is activated. Thus, the predetermined condition is satisfied after securing a sufficient time for stopping the rotation in one direction in the transport mechanism while appropriately interlocking the operation of the machine movement restricting portion and the operation of the check portion. Thus, damage to the rotation restricting portion, the transport mechanism, and the like can be effectively suppressed.

According to a sixth aspect of the present invention, the rotation restricting portion is operated in conjunction with the movement of the work operation tool to the reverse operation position, and the rotation restricting portion restricts the transport mechanism in the rotation restricting portion. Equipped with interlocking mechanism,
The check control unit is configured to be able to check that the transport mechanism is in a restriction state by checking the movement of the rotation restriction unit interlocking mechanism until the predetermined condition is satisfied.
The rotation control unit interlocking mechanism restricts the movement of the check control unit in a state where the work operation tool is positioned at the reverse rotation operation position and the transport mechanism is in the control state, thereby the machine movement control unit It is in the point that switching from the operating state to the non-operating state is disabled.

  According to this configuration, by providing the rotation restricting portion interlocking mechanism, the movement restricting state of the transport mechanism can be set in the rotation restricting portion while simplifying the structure by utilizing the movement of the work operation tool. . Moreover, since the check control unit checks the movement of the rotation restricting unit interlocking mechanism to check that the transfer mechanism is in the restriction state, the rotation restricting unit restricts the rotation of the transfer mechanism to the restriction state. The partial interlocking mechanism can be used to appropriately restrain the transport mechanism from being in the restricted state. Furthermore, since the rotation restricting part interlocking mechanism restricts the movement of the check control part, switching of the machine movement restricting part from the operation state to the non-operation state is not possible. The unit has three functions: a function to put the transport mechanism in the restricted state, a function to switch the check part to the check state, and a function to disable the switch on the machine movement restriction part to the inoperative state. The respective functions can be appropriately exhibited while efficiently simplifying the configuration.

It is a left side view of the combine concerning one embodiment of the present invention. It is a right side view of the combine concerning one embodiment of the present invention. It is a top view of the combine concerning one embodiment of the present invention. It is a figure showing the power transmission composition in the combine concerning one embodiment of the present invention. It is a left side view showing the composition concerning the feeder concerning one embodiment of the present invention, and its neighborhood. It is a left side view showing the composition of the feeder concerning one embodiment of the present invention. It is a top view showing the back of the feeder concerning one embodiment of the present invention. It is a perspective view showing the back of the feeder concerning one embodiment of the present invention. It is a perspective view showing composition of a reversal mechanism concerning one embodiment of the present invention. It is a left side view showing a reversing mechanism concerning one embodiment of the present invention. It is a top view showing the reversal mechanism and amplification mechanism concerning one embodiment of the present invention. It is back surface sectional drawing which shows the reversing mechanism and amplification mechanism which concern on one Embodiment of this invention. It is a schematic diagram which shows the inversion mechanism and amplification mechanism which concern on one Embodiment of this invention. It is a figure showing composition of a work clutch lever concerning one embodiment of the present invention. It is explanatory drawing about the operation aspect of the work clutch lever which concerns on one Embodiment of this invention. It is a perspective view showing a work clutch lever and a link mechanism concerning one embodiment of the present invention. It is a top view showing the work clutch lever concerning one embodiment of the present invention, and a link mechanism. It is a side view showing a work clutch lever concerning one embodiment of the present invention, a link mechanism, and a check control part. It is a side view showing a work clutch lever concerning one embodiment of the present invention, a link mechanism, and a check control part. It is a side view showing a work clutch lever concerning one embodiment of the present invention, a link mechanism, and a check control part. It is a control block diagram concerning one embodiment of the present invention. It is operation | movement explanatory drawing of the operation | work clutch lever which concerns on one Embodiment of this invention, and a link mechanism. It is operation | movement explanatory drawing of the reversing mechanism which concerns on one Embodiment of this invention.

  According to the present invention, in the configuration in which the transport device for transporting the grain scraps cut off by the reaper and supplying it to the threshing portion is provided rotatably and vertically with the reaper input shaft as a rotation axis, It is an object of the present invention to make it possible to eliminate the clogging of cereal grains in the transfer device by a simple structure by enabling the operation of the transfer device in the reverse direction of the transfer device. Hereinafter, embodiments of the present invention will be described.

[Overall composition of combine]
First, the overall configuration of the combine 1 according to the present embodiment will be described using FIGS. 1 to 4. In the following description, the left side (lower side in FIG. 3) and the right side (upper side in FIG. 3) of the combine 1 are referred to as the left side and the right side of the combine 1, respectively.

  As shown in FIG. 1 and FIG. 2, the combine 1 according to the present embodiment is a harvester that scrapes the crop of the cropped field into the machine body, and threshs / sorts / stores the grain and can be carried out of the machine as appropriate. It is an ordinary type combine as. The combine 1 has a traveling machine body 2 (corresponding to a machine body) capable of self-propelled travel and a reaper 3 provided at the front end of the traveling machine body 2. The reaper 3 is configured as a reaper that takes in uncut grain pods such as rice and wheat while harvesting, and is attached to the traveling machine body 2 so as to be able to move up and down.

  The traveling body 2 includes a traveling unit 4 configured as a crawler-type traveling device having a pair of left and right crawler units 5 and 5. An airframe frame 6 is provided between the left and right crawlers 5 and 5. Each crawler unit 5 has a plurality of rotating bodies including a drive sprocket 5a provided at the front end and a tension roller 5b provided at the rear end of the crawler 5, and a crawler belt 5c wound around these rotating bodies. And. A plurality of rotating bodies constituting the crawler unit 5 are provided on a track frame 5 d provided on the lower surface side of the traveling machine body 2. In addition, the drive sprocket 5 a is rotationally driven in response to the transmission of the power of the engine 25 provided in the combine 1.

  As shown in FIGS. 1 to 3, on the left side of the machine frame 6, a threshing part 7 for threshing a grain scrap supplied by being cut off by the mowing part 3, and a grain threshed by the threshing part 7 are selected A sorting unit 8 is provided. The threshing unit 7 and the sorting unit 8 are disposed in a mode in which the threshing unit 7 is at the upper stage and the sorting unit 8 is at the lower stage.

  As shown in FIGS. 2 and 3, on the right side of the threshing unit 7 and the sorting unit 8 on the airframe frame 6, a gren tank 10 for storing grains (cleared grains) sorted by the sorting unit 8 is provided. A grain storage 9 is provided. In the glen tank 10, the lower discharge conveyor 11 which conveys a storage grain toward the discharge port of the gren tank 10 is provided (refer FIG. 4). A vertical conveyance conveyor 12 is vertically provided so as to communicate with the discharge port of the grain tank 10. At the upper end portion of the vertical transfer conveyor 12, a grain discharging conveyor 13 is connected. The grain discharging conveyor 13 is provided so as to be horizontally rotatable and vertically rockable about a horizontal axis. Grains in the gren tank 10 are conveyed by these conveyors, and are discharged from a weir mouth 14 provided at the tip of the grain discharge conveyor 13 to a truck bed or a container of a truck.

  In addition, as shown in FIGS. 1 to 3, on the body frame 6, the operation portion 15 on which the operator rides is located at the front position of the grain storage portion 9, that is, the position of the right front on the body frame 6. It is provided. The driving unit 15 is covered by a cabin 16. The driver's seat 17, a steering handle 18 disposed in front of the driver's seat 17, a main transmission lever 21, an auxiliary transmission lever 22, a working clutch lever 23 and the like are provided in the driving unit 15. The work clutch lever 23 is a work operation tool for turning on and off the threshing clutch 57 and the reaper clutch 75 (see FIG. 4). The main shift lever 21, the sub shift lever 22, and the working clutch lever 23 are disposed on a lever column 24 provided on the left side of the driver's seat 17.

  As shown in FIGS. 2 and 3, an engine 25 as a drive source is provided behind the grain storage portion 9 on the traveling airframe 2. The engine 25 is a diesel engine and is equipped with a diesel particulate filter (DPF) 26 (see FIG. 1) which is an exhaust gas purification device. The DPF 26 collects particulate matter and the like mainly composed of black smoke in exhaust gas discharged from the engine 25. The engine 25 purifies the exhaust gas by passing the exhaust gas into the DPF 26.

  The reaper 3 will be described. As shown in FIGS. 1 to 3, the reaper 3 includes a feeder 30 as a transport device, a grain header (platform) 31, a cutting blade device 32, a pair of left and right branched bodies 33 and 33, and a scratching reel And 34.

  The feeder 30 is a transport device that transports the grain scraps that have been cut by the reaper 3 and supplies it to the threshing part 7. The feeder 30 has a feeder house 35 as a housing, and a conveyor 36 (see FIG. 5) provided in the feeder house 35 for transporting cereals. The feeder 30 is located on the left side of the cabin 16 and has a rear end opening of a feeder house 35 formed in a substantially square cylindrical shape having a longitudinal direction in the front and rear direction in plan view to the front throttling port 7a of the threshing part 7. It is provided in communication.

  As shown in FIGS. 1 to 3, the grain header 31 is formed in a horizontally long bucket shape and is continuously provided on the front side of the feeder 30 so as to communicate with the front end opening of the feeder house 35. In the grain header 31, a scraping auger (platform auger) 37 is provided. The scraping auger 37 is rotatably supported with the left and right direction as the rotation axis direction.

  The cutting blade device 32 is provided at the front lower end edge of the grain header 31 and is configured like a hair clipper. The pair of left and right wefts 33, 33 are provided to project forward from the front left and right sides of the grain header 31. The take-up reel 34 is a reel with a tine bar, and is provided at an upper front position of the take-up auger 37. The take-up reel 34 is rotatably supported between the end portions of a pair of left and right reel support arms 34a and 34a whose base end portions are pivotally supported by the grain header 31 with the left and right direction as the rotation axis direction. The take-up reel 34 continuously acts on the setting portion of the grain stalk while rotating and scrapes the set-up portion of the grain stalk into the side of the auger 37. For the operation of each part of the reaper 3, power of the engine 25 transmitted through various transmission mechanisms is used.

  As shown in FIG. 1, the conveyor 36 (see FIG. 5) in the feeder house 35 is provided at the front of the threshing part 7 as a drive shaft for pivotally supporting the feed end side thereof. An input shaft (feeder house conveyor shaft) 38 is provided. The rear end portion of the feeder 30 is rotatably supported by the reaper input shaft 38 with the left and right direction as the rotational axis direction. Further, a lifting cylinder 39 is interposed between the lower surface of the feeder house 35 and the machine frame 6.

  As shown in FIG. 1 and FIG. 2, the lifting cylinder 39 is a single acting hydraulic cylinder that has the action of hydraulic pressure when it is extended. Therefore, the raising and lowering cylinder 39 extends with the action of the hydraulic pressure, whereby the reaper 3 (feeder 30) rotates in the upward direction, and the oil pressure of the raising and lowering cylinder 39 is released. The lifting cylinder 39 is shortened as the feeder 30) lowers by its own weight.

  With such a configuration, the reaper 3 is provided so as to move up and down with the reaper input shaft 38 as a rotation support shaft by the expansion and contraction operation of the elevating cylinder 39. That is, the rear end portion of the feeder 30 is rotatably supported on the traveling machine body 2 side of the combine 1 with the reaper input shaft 38 as a rotation axis. And the feeder 30 comprises the cutting part 3 with the cutting blade apparatus 32, the taking-in reel 34 grade | etc., Provided in the front side, The cutting part 3 is the feeder 30 with respect to the traveling body 2 by the expansion-contraction operation | movement of the cylinder 39 for raising / lowering. It is configured to move up and down by turning. The elevating operation of the feeder 30 is operated by a predetermined operation unit provided in the operation unit 15.

  The threshing unit 7 and the sorting unit 8 will be described. As shown in FIG. 1, the threshing unit 7 has a threshing drum 41 provided in a throttling chamber in which the throttling opening 7 a is opened on the front side, and a mesh 42 disposed below the threshing drum 41. The threshing cylinder 41 is rotatably supported by a threshing cylinder shaft 41 a whose axial direction is the front-rear direction. The threshing cylinder 41 has a cylindrical main body in which a threshing barrel shaft 41a (see FIG. 4) is aligned with the central axis, and a spiral blade is provided on the outer peripheral surface of the main body. On the upper side of the threshing cylinder 41, a plurality of dust transfer valves (not shown) for adjusting the transport speed (retention time) of the grain removal in the throttling chamber are provided to be adjustable in angle. The receiving net 42 leaks the grain and is provided along the outer peripheral surface of the lower part of the threshing drum 41.

  The sorting unit 8 is a swing sorting disc 43 (see FIG. 4) as a swinging part disposed below the mesh 42 and a swing shaft that swings the swing sorting disc 43 by rotational power from a drive source. It has a swing mechanism 44 including 44a (refer to FIG. 4), a first conveyor 45, a second conveyor 46, and a balustrade 47. Note that, as shown in FIG. 4, a pre-fan 71 is provided in front of the tomb 47, and a second fan 72 is provided behind the torn 47.

  The rocking sorting board 43 (see FIG. 4) has a configuration for specific gravity sorting such as a feed pan, a chaff sieve disposed behind the feed pan to control the amount of grain leakage, and a glen sheave disposed below the chaff sieve. The first conveyor 45 (see FIG. 4) is disposed in the first weir extending in the widthwise direction of the machine so as to concentrate the first grains. The second conveyer 46 (see FIG. 4) is disposed at a position rearward of the conveyor 45 in a second pot extending in the widthwise direction of the machine so as to collect second grains. The tangerine 47 blows a sort of air which passes through the front lower side and the rear upper side to the swinging sorting board 43.

  Further, a reduction conveyor 48 is provided on the left side of the machine of the threshing unit 7 and the sorting unit 8. The reduction conveyor 48 is positioned with its lower end in the vicinity of the second conveyor 46 and connected to the second conveyor 46, and has its upper end positioned in the vicinity of the front end of the threshing drum 41 and extends in an upward sloping shape. It is set up. Further, an upper conveyor 49 (see FIG. 4) extending in the left-right direction in front of the threshing drum 41 is provided at the upper end portion of the reduction conveyor 48.

  The combine 1 having the above-described configuration has a desired height (harvest crop) with respect to the reaper 3 by the elevating operation of the feeder 30 centering on the reaper input shaft 38 (support shaft) in the field The height is raised to the harvest height of the grain scale, and the operation state is changed from the non-operation state, and the traveling vehicle 2 travels in that state. As a result, combine 1 separates the harvest crop into a target to be cut and a target not to be cut by the left and right separating bodies 33 and 33, and scrapes the landing portion on the tip side of the grain to be cut with scraping reel 34 While cutting, the remnant part of the grain crucible is cut off by the cutting blade device 32.

  The landing portion of the grain remnant cut off at the desired harvesting position is scraped into the grain header 31 by the rotationally driven scraping auger 37, and collected near the entrance of the feeder house 35 at the left and right center of the grain header 31. Then, it is introduced into the throttling port 7 a through the feeder house 35 by the conveyor 36 in the feeder house 35 and supplied to the threshing unit 7.

  The anchorage portion of the grain gravel supplied to the threshing portion 7 is threshed by the threshing portion 7. Specifically, the grain gravel supplied to the threshing unit 7 is mainly threshed between the threshing drum 41 and the net 42 while being transported rearward by the rotating threshing drum 41. De-graining, such as grains smaller than the mesh of the receiving net 42 leaks from the receiving net 42. Scales and the like that do not leak from the mesh 42 are discharged to the field from a dust outlet provided at the rear of the sorting unit 8 by the transport action of the threshing cylinder 41.

  On the other hand, the grain threshed by the threshing part 7 and leaked from the net 42 is sorted by the sorting part 8. Specifically, the de-grained threshed by the threshing cylinder 41 and leaked from the net 42 is a grain such as a fine grain by the specific gravity sorting action by the swing sorting board 43 and the wind sorting action by the karma 47 (First item), a mixture of grains such as a grain with a branch and a grain (a second thing) and grains, and the like are separated and taken out.

  Grains (first objects) dropped from the rocking sorting board 43 by sorting in the sorting unit 8 are transported to the grain tank 10 by the conveyor 45 and the grain feeding conveyor (not shown) connected to this. . The second product is returned to the threshing start side of the threshing drum 41 by the second conveyor 46 and the reduction conveyor 48 and the upper conveyor 49 connected to it and subjected to the threshing process again. Scales and the like are discharged from the dust outlet provided at the rear of the sorting unit 8 to the field.

  Next, the power transmission configuration of the combine 1 according to the present embodiment will be described using FIG. 4. The combine 1 drives the mowing part 3, the traveling part 4, the threshing part 7, the sorting part 8 and the grain storage part 9 by the rotational power of the engine 25.

  The rotational power of the output shaft 25 a of the engine 25 is transmitted to the first counter shaft 51 by a first belt transmission mechanism 52 provided between the output shaft 25 a and the first counter shaft 51. On the other hand, the rotational power of the engine 25 is transmitted via the auger clutch 53 to the grain storage unit 9 including various conveyors such as the lower discharge conveyor 11, the vertical conveyance conveyor 12, and the grain discharge conveyor 13. The engine 25 has a working machine pump shaft for driving the charge pump 54 for operating the elevating cylinder 39 and the like.

  The rotational power transmitted from the output shaft 25 a of the engine 25 to the first countershaft 51 is branched into a power transmission system to the threshing unit 7 and a power transmission system to the traveling unit 4, the sorting unit 8 and the reaper unit 3. .

  First, regarding the power transmission system to the threshing unit 7, the rotational power of the first countershaft 51 is transmitted to the first rotor drive shaft 56 by the second belt transmission mechanism 55. The second belt transmission mechanism 55 is provided with a threshing clutch 57 that transmits the rotational power of the first countershaft 51 arbitrarily and intermittently to the first rotor drive shaft 56.

  The rotational power of the first rotor drive shaft 56 is transmitted to the rotor drive shaft 59 via the threshing transmission 58, and the rotational power of the rotor drive shaft 59 is transmitted to the threshing drum shaft 41a via the third belt transmission mechanism 60. Be done. The threshing transmission 58 has a two-stage structure having a high speed gear train and a low speed gear train, and is appropriately controlled by a predetermined actuator under the control of the control device included in the combine 1 according to the type of crop to be treated, etc. The shift operation is made.

  With such a configuration, the driving force of the engine 25 is transmitted to the threshing unit 7 including the threshing cylinder 41 and the like. Then, the threshing clutch 57 is turned ON / OFF by the operation of the work clutch lever 23, and power transmission to the threshing portion 7 is interrupted.

  Next, regarding the power transmission system to the traveling unit 4, the rotational power of the first countershaft 51 is transmitted to the second countershaft 62 by the fourth belt transmission mechanism 61. The rotational power of the second counter shaft 62 is transmitted to the HST input shaft 64 via the fifth belt transmission mechanism 63 and is input to the transmission 65 including the traveling HST and the turning HST by the HST input shaft 64. Here, “HST” is a hydraulic stepless transmission that adopts a method of converting a hydraulic pressure generated by driving a hydraulic pump into a rotational force again using a hydraulic motor. The driving sprocket 5 a of the crawler unit 5 constituting the traveling unit 4 is rotationally driven by the driving force of the transmission 65.

  Further, regarding the power transmission system to the sorting unit 8, the rotational power of the second counter shaft 62 is transmitted to the first PTO drive shaft 67 by the sixth belt transmission mechanism 66, and the rotational power of the first PTO drive shaft 67 is a gear etc. And is transmitted to the second PTO drive shaft 69 via a transmission mechanism 68 including the The rotational power of the second PTO drive shaft 69 is a pre-fan shaft 71a for rotating the pre-fan 71 by a predetermined transmission mechanism, a lug shaft 47a for rotating the lug 47, and a first conveyor shaft 45a for rotating the conveyor 45 most. Each is transmitted. Further, the rotational power of the second PTO drive shaft 69 is transmitted to the swinging shaft 44a of the swinging mechanism 44 via the conveyor shaft 45a. Further, the rotational power of the conveyor shaft 45a is transmitted to the second fan shaft 72a that rotates the second fan 72 by a predetermined transmission mechanism.

  The rotational power of the swinging shaft 44a is transmitted to a second conveyor shaft 46a that rotates the second conveyor 46 by a predetermined transmission mechanism. The rotational power of the second conveyor shaft 46a is transmitted to the vertical conveyor shaft 48a that causes the reduction conveyor 48 to rotate by a predetermined transmission mechanism, and the rotational power of the vertical conveyor shaft 48a causes the upper conveyor 49 to rotate by the predetermined transmission mechanism. It is transmitted to the conveyor shaft 49a.

  Then, regarding the power transmission system to the reaper 3, the rotational power of the second PTO drive shaft 69 is transmitted to the reaper input shaft 38 by the seventh belt transmission mechanism 73. The rotary drive of the reaper input shaft 38 operates the conveyor 36 in the feeder house 35. The seventh belt transmission mechanism 73 is provided with a reaper clutch 75 for optionally transmitting the rotational power of the second PTO drive shaft 69 to the reaper input shaft 38 intermittently. At the right end of the reaper input shaft 38, a pulley 73a constituting a seventh belt transmission mechanism 73 is fixed.

  The rotational power of the reaper input shaft 38 is transmitted to the PF drive shaft 77 by the first chain transmission mechanism 76. The rotational power of the PF drive shaft 77 is transmitted to the PF auger shaft 37 a that rotates the scraping auger 37 via the second chain transmission mechanism 78. Further, the rotational power of the PF drive shaft 77 is transmitted to the cutting blade drive shaft 32 a that drives the cutting blade device 32 via the eighth belt transmission mechanism 80. Further, the rotational power of the PF drive shaft 77 is transmitted to the reel shaft 34 b that rotates the take-up reel 34 by the power transmission mechanism including the first reel counter shaft 81 and the second reel counter shaft 82.

  With such a configuration, the driving force of the engine 25 is transmitted to the reaper 3. Then, the reaper clutch 75 is turned on / off by the operation of the work clutch lever 23, and power transmission to the reaper 3 is interrupted.

  The combine 1 according to the present embodiment having the above-described configuration uses the lifting and lowering operation of the feeder 30 to eliminate the clogging of the grain scale in the feeder 30 as the transfer device by the simple structure. And a reverse conveyor operation mechanism unit for operating in the reverse direction. That is, the combine 1 is provided with the feeder 30 in the reaper 3, and the feeder 30 is provided rotatably elevatingly with the reaper input shaft 38 as a rotation axis, the conveyor reverse direction operating mechanism portion The conveyor 36 is operated in the reverse direction by the raising and lowering operation. The conveyor reverse direction operating mechanism will be described below with reference to FIGS. 5 to 10.

  In the combine 1 according to the present embodiment, the feeder 30 has a conveyor 36 (corresponding to a transport unit) having a reaper input shaft 38 as a drive shaft that receives power transmission with the horizontal direction as an axial direction in the feeder house 35. It is provided so as to move up and down by rotating around a reaper input shaft 38 (corresponding to a transport mechanism) with respect to the machine of the combine 1. That is, as described above, the feeder 30 is provided to move up and down about the reaping input shaft 38 by the expansion and contraction of the elevating cylinder 39 provided between the feeder house 35 and the machine body frame 6 ( See FIG. 5, arrow A1).

  As shown in FIGS. 6 and 7, the feeder house 35 has left and right side surface portions 91L and 91R, a lower surface portion 92, and an upper surface portion 93, and these surface portions constitute a cylindrical body having both front and rear openings. doing. More specifically, as shown in FIG. 5, the upper surface portion 93 has an inclined planar rear side surface portion 93a and a front side surface portion 93b, and has a bent surface shape with the front and rear central portion as the top in a side view. Corresponding to the curved surface shape of the upper surface portion 93, the left and right side surface portions 91L and 91R (see FIGS. 6 and 7) have an upper portion in a mountain shape.

  In such a feeder house 35, a substantially horizontally elongated rectangular opening is formed by the rear end portions of the left and right side surface portions 91L and 91R, the lower surface portion 92, and the rear side surface portion 93a of the upper surface portion 93 at the rear end. The part 94 is formed (see FIG. 8). The front end of the elevating cylinder 39 is rotatably supported by the shaft support 39 a with respect to the front of the lower surface 92 of the feeder house 35 with the left and right directions as the rotational axis.

  As shown in FIGS. 5 to 8, the conveyor 36 is a chain conveyor having chains 95 provided in parallel with each other on the left and right sides in the feeder house 35 and a plurality of plates 96 provided between the left and right chains 95. is there. The plate 96 is provided on the outer peripheral side of the chain 95. The plate 96 is an elongated member whose longitudinal direction is the installation direction (left and right direction) between the left and right chains 95, and is a bent plate-like member having a crank-like or substantially "U" -like cross-sectional shape. The plate 96 is fixed to the chain 95 by fasteners such as bolts. In the present embodiment, fifteen plates 96 are attached to the chain 95 at predetermined intervals in the longitudinal direction of the chain 95.

  As shown in FIG. 7 and FIG. 8, the conveyor 36 is a sprocket provided so as to rotate integrally with the reaper input shaft 38 on the left and right sides of the installation portion in the feeder house 35 of the reaper input shaft 38 as its drive shaft. At 97, wind the rear portion of the chain 95. On the other hand, as shown in FIGS. 5 and 6, the front portion of the chain 95 is wound around a cylindrical front drum 98 provided at the front end in the feeder house 35. The front drum 98 is rotatably supported centering around a conveyor driven shaft 98 a which is a predetermined rotation axis whose axial direction is in the left-right direction between the left and right side surface portions 91 L, 91 R of the feeder house 35. That is, the chain 95 is endlessly wound around the sprocket 97 and the front drum 98, and the rotation of the sprocket 97 accompanying the rotation of the reaper input shaft 38 moves the plate 96 while maintaining the winding state. To drive. The conveyor 36 causes the rear end of the sprocket 97 to project from the opening 94 (see FIG. 8) on the rear side of the feeder house 35 and causes the front end of the front drum 98 to project slightly from the front opening of the feeder house 35. It is provided as.

  With such a configuration, the conveyor 36 is driven in the forward direction (FIG. 6, FIG. 6) by rotating the reaping input shaft 38 in a counterclockwise direction (left rotation direction) in left side view (see FIG. 6, arrow B1). , See arrow B2), the grain scale taken into the feeder house 35 by the scraping auger 37 is hooked on the plate 96 and conveyed diagonally upward and backward. That is, when the conveyor 36 is driven in the forward direction, the path portion of the linear chain 95 located below the sprocket 97 and the front drum 98 (the chain 95 located immediately above the lower surface 92 of the feeder house 35 The path portion) is the forward path portion moving from the front side to the rear side, and the path portion of the straight chain 95 located above the sprocket 97 and the front drum 98 is the return path portion moving from the rear side to the front side. The cereal grits transported by the conveyor 36 are supplied from the feeder house 35 to the threshing unit 7 through the throttling port 7a (see FIG. 1).

  As shown in FIG. 7, at the rear end of the feeder house 35, the reaper input shaft 38 is bridged between the left and right side portions 91L and 91R and protrudes outward from the side portions 91L and 91R. The reaper input shaft 38 is provided rotatably relative to the feeder house 35 via a bearing member or the like. The both ends of the reaper input shaft 38 are rotatably supported via support members or the like with respect to support brackets 100 (100L, 100R) provided on the left and right sides of the rear end of the feeder house 35, respectively. .

  As shown in FIG. 8, the support bracket 100 is a member whose longitudinal direction is in the vertical direction, and a bent plate-like base portion having a substantially “L” shape in plan view by the fixed surface portion 101 and the support surface portion 102; A plurality of horizontal plate-like ribs 103 are provided inside the bent shape of the base portion. The support bracket 100 has a fixed surface portion 101 which is a flat plate portion forming one side in a substantially L-shaped plan view shape in the base portion and is directed to the rear side, and a substantially L-shaped plan view shape as well. It is provided in the state which turned the support surface part 102 which is a flat part which makes the other side part in in the inside of right and left.

  The left and right support brackets 100L, 100R align the support surface 102 along the outer surfaces of the side surfaces 91L, 91R of the feeder house 35 on the left and right outer sides of the feeder house 35, and make the support surfaces 102 face each other. They are disposed so as to be substantially symmetrical to each other. That is, the left and right support brackets 100L and 100R are provided in such a manner that the rear end portion of the feeder house 35 is sandwiched between the support surface portions 102 from the left and right sides.

  Further, the support bracket 100 is provided in a state of being fixed to the main machine side of the combine 1. Specifically, the support bracket 100 is fixed to the left and right support columns 105 (105L, 105R) provided on the main unit side of the combine 1. The support columns 105 are members constituting the machine frame of the combine machine 1 and are provided in front of the threshing unit 7 at two places on the left and right sides of the traveling airframe 2. The left support bracket 100L is fixed to the front of the top of the left support column 105L, and the right support bracket 100R is fixed to the top of the right support column 105R.

  The support bracket 100 is fixed to the support 105 in a state in which the fixed surface 101 is in contact with the front surface of the support 105 by fastening members 106 such as a plurality of bolts penetrating the fixing surface 101 from the front side. In the present embodiment, each support bracket 100 is fixed to the support column 105 by four fastening members 106 disposed at predetermined intervals in the vertical direction.

  As described above, the feeder 30 is vertically movably supported with respect to the support bracket 100 fixed to the support 105 which is the configuration of the combine 1 on the main unit side, with the left and right direction as the axial direction. That is, the feeder 30 is provided so as to rotate up and down with respect to the machine side with the reaper input shaft 38 as a rotation axis in a mode in which the rear end portion is sandwiched from the left and right by the left and right support brackets 100L and 100R. There is.

  In addition, as shown in FIG. 5, FIG. 6 and FIG. 8, in front of the upper part of the support bracket 100L on the left side, the cutting height of the feeder house 35 (height of the reaper 3 with respect to this machine) A reaper position sensor 107 for detecting is provided. As shown in FIGS. 8 and 9, the reaper position sensor 107 is attached to a sensor support stay 108 provided in front of the fixed surface portion 101 of the support bracket 100L, and is supported on the side of the machine. The sensor support stay 108 is the above-described two fastenings via a cylindrical sleeve body 106 a that allows the upper two fastening members 106 of the four fastening members 106 to secure the support bracket 100 L to the machine side. It is fixed and supported by the member 106.

  As shown in FIGS. 9 and 10, the reaper position sensor 107 has a detection piece 107a provided rotatably in an axial direction in the left-right direction and projecting forward. On the other hand, a rod-like detection pin 109 acting on the detection piece 107a is provided in a protruding manner on the left side surface portion 91L of the feeder house 35. The detection pin 109 is located on the upper side of the detection piece 107a, and acts on the detection piece 107a within a predetermined operation range in the lifting and lowering operation of the feeder 30 to rotate the detection piece 107a. With such a configuration, the reaper position sensor 107 detects the cutting height based on the amount of rotation of the detection piece 107 a that receives the action of the detection pin 109 in the lifting and lowering operation of the feeder 30.

  The combine 1 having the configuration as described above is a conveyor reverse operation mechanism that operates the conveyor 36 of the feeder 30 in the reverse direction by using the elevating operation of the feeder 30, and the raising operation of the feeder 30 is applied to the reaper input shaft 38 Transmitting and moving the reaper input shaft 38 along with the raising operation of the feeder 30 in the reverse direction (hereinafter referred to as "the forward direction") when transporting the grain (when the conveyor 36 is driven in the forward direction). Reverse rotation direction (refer to FIGS. 8 and 9). That is, in the state where the feeder 30 is lowered from the rising end position of its raising and lowering operation, the feeder house 35 and the reaper input shaft 38 are engaged by the reverse mechanism 110 and the normal direction of the reaper input shaft 38 with respect to the feeder house 35 Relative rotation is restricted. By raising the feeder 30 in this state, the reaper input shaft 38 rotates in the reverse direction together with the feeder house 35.

  According to the reversing mechanism 110, the following actions can be obtained in detail. The reaper input shaft 38 is supported on the main unit side of the combine 1 via the left and right support brackets 100 as described above, and is provided so as to be rotatable relative to the feeder house 35. Further, as described later, the gear 120 which is a member constituting the reverse rotation mechanism 110 is supported by the reaper input shaft 38, and the claw member 130 which is a member similarly constituting the reverse rotation mechanism 110 is supported by the feeder house 35 side. ing.

For this reason, when the relative rotation of the reaper input shaft 38 relative to the feeder house 35 in the forward rotation direction is restricted by the reverse rotation mechanism 110, when the feeder 30 rotates upward with the reaper input shaft 38 as a rotational center, the feeder 30 The reaper input shaft 38 is forcibly rotated together with the feeder house 35 in the reverse direction by the amount of the upward turning amount. That is, the direction of upward rotation of the feeder house 35 (see arrow C1 in FIG. 6) is clockwise (rightward rotation direction) in left side view. The normal direction of the reaper input shaft 38 (see arrow C2 in FIG. 6) And the reaper input shaft 38 engaged with the feeder house 35 by the reverse mechanism 110 rotates in the reverse direction integrally with the feeder house 35 rotating upward.

  Therefore, as the reversing mechanism 110 for rotating the reaping input shaft 38 in the reverse direction using the elevating operation of the feeder 30, any configuration may be used as long as the above-mentioned engagement with the reaping input shaft 38 can be obtained. That is, in the configuration in which the reaper input shaft 38 supported on the side of the machine rotates relative to the feeder house 35 as the reverse rotation mechanism 110, the relative rotation of the reaper input shaft 38 at least in the forward rotation direction. Any configuration may be used as long as it functions to restrict rotation. Hereinafter, the specific configuration of the reversing mechanism 110 according to the present embodiment will be described.

As shown in FIG. 5 to FIG. 8, the reversing mechanism 110 is provided on the left side, which is the outer side in the left-right direction of the combine machine, of the right and left sides of the feeder house 35. That is,
In the present embodiment, the feeder 30 is provided on the left side of the cabin 16, and the left side of the feeder house 35 is on the outer side in the left-right direction of the machine of the combine 1 and on the left side of the rear end of the feeder house 35. , A reversing mechanism 110 is provided.

  The reversing mechanism 110 has a gear 120 as a first engagement member supported by the reaper input shaft 38 and a claw member 130 engaged with the gear 120. The reversing mechanism 110 is configured to include a ratchet mechanism that limits the lifting and lowering operation of the feeder 30 for rotating the reaper input shaft 38 via the gear 120 to the lifting and lowering operation of the feeder 30.

  As shown in FIGS. 9 and 10, the gear 120 is supported by a left projecting portion 38a (see FIG. 12) of the reaper input shaft 38 from the inside of the feeder house 35. The gear 120 is an annular plate-like member which allows the reaper input shaft 38 to pass through, and has a plurality of teeth 121 on the outer peripheral side of the main body portion which is the inner peripheral side portion. The teeth 121 have a mountain shape having a substantially triangular shape when viewed in the rotational axis direction of the gear 120. Between the teeth 121 adjacent to each other in the circumferential direction of the gear 120, an engagement recess 122 having a substantially "V" shape is formed as viewed in the rotational axis direction of the gear 120.

  As shown in FIG. 5 to FIG. 8, the claw member 130 is provided in a state of being supported by the feeder 30, and by engaging with the gear 120, the raising operation of the feeder 30 via the gear 120 is the mowing input shaft Communicate to 38. The claw member 130 is provided on the left side of the feeder house 35 at a position in front of the gear 120. The claw member 130 is a plate-like member having a predetermined shape, and is rotatably provided with the plate thickness direction as the left-right direction. The claw member 130 has a thickness substantially the same as or thinner than that of the gear 120, and is provided at a position substantially the same as the position of the gear 120 so as to be engageable with the gear 120 ( See Figure 7).

  As shown in FIGS. 7 and 9, the claw members 130 are provided in a state of being rotatably supported with respect to the left side surface portion 91L of the feeder house 35 that constitutes the feeder 30. The claw member 130 is rotatably supported with a left and right direction as a rotation axis direction by a support shaft 131 having a left and right direction as an axial direction and protruding leftward from the side surface portion 91L.

  As shown in FIGS. 9 and 10, the support shaft 131 is a cylindrical portion, and the projecting tip end portion is a reduced diameter portion 131a, and the reduced diameter portion 131a is penetrated by the claw member 130 and the reduced diameter portion 131a. The claw member 130 is rotatably supported by receiving the fitting of the retaining ring 135b through the washer 135a. Further, the support shaft 131 receives support of a support stay 136 for reinforcement provided between the side surface portion 91L and the front lower side.

  The claw member 130 is a support portion by the support shaft 131, and has a support base 132 through which the support shaft 131 penetrates, and a claw main body 133 projecting upward from the support base 132. The support base 132 has a shape protruding around the support shaft 131, and the claw main body portion 133 is provided on the upper side of the support base 132. The claw body portion 133 has a shape bent toward the rear side from the upper side of the support base 132, and has at its tip end a sharp engagement portion 134 having a sharp angle toward the rear side where the gear 120 is positioned. The claw member 130 engages with the gear 120 by fitting the sharp engagement portion 134 into the engagement recess 122 of the gear 120. The sharp engagement portion 134 has an outer shape corresponding to the substantially “V” -shaped concave shape of the engagement recess 122 so as to fit the engagement recess 122.

  With such a configuration, the claw member 130 is engaged with the engagement concave portion 122 positioned on the front side of the gear 120 by rotating in the clockwise direction (right rotation direction) in left side view. And engage the gear 120. On the other hand, when the claw member 130 in a state engaged with the gear 120 rotates counterclockwise (left rotation direction) in the left side view, the engagement of the claw member 130 with the gear 120 is released.

  The claw member 130 is biased by a spring 140 as a biasing member in a direction of engagement with the gear 120, that is, in a right rotation direction (hereinafter referred to as "engagement direction") in left side view. The spring 140 is a tension coil spring and exerts an action of pulling the claw member 130 in the engagement direction with respect to the claw member 130. The spring 140 is provided on the lower rear side (the lower right side in FIG. 10) with respect to the claw member 130, and by pulling the rear side portion of the claw member 130 downward, the claw member 130 is engaged by elastic force. Energize in the same direction.

  Specifically, the spring 140 passes through the hook portion 140a on the upper end side which is the one end side, a locking pin 141 which penetrates a portion on the rear side (right side in FIG. 10) of the support portion by the support shaft 131 of the claw member 130. It is locked to A hook portion 140a on the upper end side of the spring 140 is hooked on a protruding portion to the right side (rear side in FIG. 10) of the locking pin 141 which penetrates the claw member 130.

  On the other hand, the hook portion 140b on the lower end side, which is the other end side of the spring 140, is engaged with the support stay 142 fixed to the side surface portion 91L of the feeder house 35 by welding or the like. The support stay 142 is provided at a position below the claw member 130. The support stay 142 is a bent plate-like portion having a predetermined bent shape that protrudes leftward from the side surface portion 91L, and is disposed behind the horizontal plate portion 142a and the horizontal plate portion 142a along the downward slope of the feeder house 35. And a vertical plate portion 142b bent upward at a right angle to the horizontal plate portion 142a from the edge.

  With respect to such a support stay 142, the spring 140 is engaged with and supported by the support stay 142 in a state in which the lower hook portion 140b is penetrated to the engagement hole 142c formed in the vertical plate portion 142b. .

  Further, the pivotal movement of the claw member 130 about the support shaft 131 is operated via the operation wire 145 as a wire member connected to the claw member 130. One end side of the operation wire 145 is connected to the claw member 130 via the connection member 146. The connecting member 146 is a longitudinal member having a substantially rectangular shape in a side view and a substantially "U" -shaped outer shape opened on the upper side in a front view, and the upper end portion thereof is a support portion by the support shaft 131 of the claw member 130. The lock pin 147 is connected to the front side (left side in FIG. 10) of the lock pin 147. The upper end portion of the connecting member 146 is connected to a protruding portion to the right side (the back side in FIG. 10) of the locking pin 147 which passes through the claw member 130. The locking pin 147 penetrates an elongated hole 146 a formed in the connecting member 146 along the longitudinal direction thereof, and is supported by the connecting member 146 by receiving the penetration of the pin. Thus, the connecting member 146 is provided so as to be movable relative to the locking pin 147 along the longitudinal direction of the long hole 146a. On the other hand, one end of the operation wire 145 is connected to the lower end of the connection member 146.

  The operation wire 145 extends through the tubular wire support member 148 fixedly supported by the horizontal plate portion 142 a of the support stay 142 and covered by the flexible covering tube 149. The wire support member 148 is fixed to and supported by the lateral plate portion 142 a by a fastening operation or the like by a nut member in a mode in which the lateral plate portion 142 a is vertically penetrated. The other end side of the operation wire 145 is a predetermined operation tool via a member constituting a predetermined link mechanism (link mechanism 300) described later, so as to be operated by a predetermined operation tool provided in the operation unit 15. It is connected.

  In the claw member 130, a locking pin 141 for locking the spring 140 to the claw member 130 and a locking pin 147 for coupling the operation wire 145 to the claw member 130 have a support position by the support shaft 131 between them. It is located on the opposite side of the front and back. That is, the locking pin 141 for the spring 140 is located rearward of the support shaft 131, and the locking pin 147 for the operation wire 145 is located forward of the support shaft 131.

  Further, between the claw member 130 and the support stay 142, the installation direction (expansion and contraction direction) of the spring 140 and the extension direction of the operation wire 145 are both forward and substantially vertical directions. The claw member 130 always receives the downward pulling action of the spring 140, and rotates like a seesaw back and forth around the support shaft 131 depending on the presence or absence of the downward pulling action of the operation wire 145.

  The operation of the reversing mechanism 110 will be described with reference to FIG. Normally, as shown in FIG. 10, the reverse rotation mechanism 110 is not operating, and the claw member 130 is in the direction opposite to the engagement direction from a rotational position (hereinafter referred to as “engagement position”) engaging with the gear 120 It is located in the non-engagement position moved to (hereinafter referred to as "anti-engagement direction"). That is, the reversing mechanism 110 is in a non-operating state, and the reaper input shaft 38 is in a non-engaging state with the feeder house 35. The state in which the claw member 130 is in the disengaged position is held by the pulling action of the operation wire 145 which pulls the claw member 130 in the reverse engagement direction against the biasing action of the spring 140 in the engagement direction.

  Then, the operation for bringing the reverse rotation mechanism 110 into the operating state is performed by the operation of the predetermined operation tool for operating the operation wire 145, whereby the pulling action of the claw member 130 by the operation wire 145 is released. Thereby, the claw member 130 is rotated in the engagement direction by the urging force of the spring 140 (see arrow D1), the claw member 130 reaches the engagement position, and the sharp engagement portion 134 is positioned on the front side of the gear 120 The engagement member 122 is fitted in the engagement recess 122, and the claw member 130 is engaged with the gear 120. That is, the reversing mechanism 110 is in the operating state, and the reaper input shaft 38 is in the engagement state with the feeder house 35.

  From the operation state of the reversing mechanism 110, the operation wire 145 is pulled by performing an operation to deactivate the reversing mechanism 110 by the operation of a predetermined operation tool. As a result, the claw member 130 rotates in the opposite engagement direction (opposite to the arrow D1) against the biasing force of the spring 140, and the engagement of the claw member 130 with the gear 120 is released, and the claw member 130 is not When the engaged position is reached, the reversing mechanism 110 returns to the inoperative state.

  In the connection structure of the operation wire 145 to the claw member 130, a play is provided in the action direction of the operation wire 145 by the structure in which the locking pin 147 is engaged with the long hole 146a of the connection member 146. Thereby, the unintended engagement etc. with respect to the gearwheel 120 of the nail | claw member 130 is prevented, and the switching operation of the reliable operation state * non-operation state of the reversing mechanism 110 is possible.

  Further, regarding the engagement structure of the gear 120 and the claw member 130, the reversing mechanism 110 reverses the direction of the reverse direction of the conveyor 36 with respect to the feeder house 35 of the gear 120 in a state where the claw member 130 is engaged with the gear 120 It has a ratchet type structure in which relative rotation in the right rotation direction is permitted in the rotation direction corresponding to Y. That is, each tooth 121 of gear 120 is a gear such that the direction of relative rotation of gear 120 with respect to feeder house 35 is restricted in the direction corresponding to the reverse rotation of reaper input shaft 38 in the operating state of reverse mechanism 110. The circumferential direction of 120 is inclined to the radial direction of the gear 120 in the forward rotation direction side of the conveyor 36 (left rotation direction side in left side view).

  According to such a configuration, for example, due to the clogging action of the grain in the feeder house 35, a state occurs in which the reaper input shaft 38 integrally rotates with the feeder house 35 along with the raising and lowering operation of the feeder house 35. In this case, when the reversing mechanism 110 is activated, the following action is obtained. That is, at the time of the raising operation of the feeder 30, the gear 120 rotates in the direction (reverse direction) corresponding to the reverse direction of the conveyor 36 along with the rising feeder house 35. On the other hand, when the feeder 30 is lowered, relative rotation of the gear 120 with respect to the feeder house 35 is permitted. The direction of relative rotation of the gear 120 here is the reverse direction. That is, when the relative rotation of the gear 120 with respect to the feeder house 35 is permitted during the lowering operation of the feeder house 35, the reaper input shaft 38 rotates relative to the feeder house 35 in the reverse direction via the gear 120. It will be. Thus, according to the ratchet structure including the gear 120 and the claw member 130, the lifting and lowering operation of the feeder 30 for rotating the reaper input shaft 38 via the gear 120 is limited to the lifting and lowering operation of the feeder 30.

  Therefore, in the operating state of the reverse rotation mechanism 110, the gear 120 pivots in the reverse direction relative to the feeder house 35 integrally with the feeder house 35 when the feeder 30 is moving upward, and when the feeder 30 is moving downward. It will be. That is, when the feeder 30 is raised or lowered, an operation of rotating the reaping input shaft 38 in the reverse direction can be obtained through the gear 120. For this reason, when the feeder 30 repeats the raising and lowering operation, an action of rotating the reaper input shaft 38 in the reverse direction can be obtained for each raising and lowering operation.

  As described above, the reverse rotation mechanism 110 according to the present embodiment includes the gear 120 supported by the reaper input shaft 38 and the claw member 130 biased in a direction (engagement direction) engaged with the gear 120. It has the ratchet mechanism which restricts the raising / lowering operation of the feeder 30 which rotates the reaper input shaft 38 via the gear 120 to the raising operation of the feeder 30.

  According to the reverse rotation mechanism 110 of the present embodiment as described above, the gear 30 supported by the reaper input shaft 38 by the amount of rotation of the feeder 30 by the upward rotation of the feeder 30 in the operation state of the reverse rotation mechanism 110 For 120, a pivoting action in the direction corresponding to the reverse direction of the reaper input shaft 38 is obtained. The rotating action of the gear 120 in the reverse direction is used, and the reaper input shaft 38 rotates in the reverse direction. As a result, the conveyor 36 operates in the reverse direction, and the clogging of the grain scale in the feeder 30 is eliminated.

  Here, for example, when the gear 120 is fixed coaxially with the reaper input shaft 38, that is, when the gear 120 is configured to rotate integrally with the reaper input shaft 38, the gear when the feeder 30 ascends The amount of rotation of 120 in the reverse direction is transmitted to the reaper input shaft 38 at 1: 1, and the conveyor 36 operates in the reverse direction. On the other hand, in the case of such a configuration, since the operation stroke of the raising and lowering operation of the feeder 30 is limited, the clogging amount of the scale is eliminated with respect to the rotation amount of the reaper input shaft 38 operating the conveyor 36 in the reverse direction. Because of this, it may not be possible to obtain a sufficient amount of rotation.

  Therefore, the combine 1 according to the present embodiment receives the transmission of the raising operation of the feeder 30 through the claw member 130, amplifies the amount of rotation of the gear 120 which is rotated, and amplifies the amount of rotation to transmit to the reaper input shaft 38. Prepare. The amplification mechanism 200 will be described with reference to FIGS. 11 to 13.

  As shown in FIG. 12, the reaper input shaft 38 is a cylindrical shaft that allows the reaper input shaft 38 to pass through the side surface portion 91L on the left side of the feeder house 35 and the support bracket 100L located on the left side of the side surface portion 91L. It is rotatably supported via the support member 201.

  The pivot support member 201 has a flange portion 201a which is an enlarged diameter portion at a portion near the right side, and the end portion on the right side is fitted into a pivot support hole 91a formed in the side surface portion 91L. Along the 91L outside surface (left side). The pivot support member 201 is fixed to the side surface 91L at a plurality of locations by fixing bolts 202 which penetrate the side surface 91L from the inside of the side surface 91L.

  Further, the shaft support member 201 has a cylindrical portion on the left side of the flange portion 201a fitted in a shaft support hole 100a formed in the support bracket 100L so as to be capable of relative rotation. The pivot support member 201 allows the protruding portion 38a from the side surface portion 91L of the reaper input shaft 38 to pass through to the left, and the reaper input shaft 38 can be relatively rotated via a bearing member 203 fixed to the reaper input shaft 38. In favor of In addition, a bearing 204 is interposed between the right end of the pivot support member 201 and the reaper input shaft 38.

  The left end portion of the reaper input shaft 38 protrudes leftward from the support bracket 100L, and the gear 120 is supported by the protruding portion 38a. The gear 120 is provided at a position close to the left side with respect to the support bracket 100L. In the operating state of the reverse rotation mechanism 110, the amplification mechanism 200 amplifies the amount of rotation of the gear 120 along with the ascent of the feeder 30 and transmits it to the reaper input shaft 38.

  The amplification mechanism 200 has an input shaft side gear supported by the reaper input shaft 38, an idler shaft 215 as a transmission shaft provided parallel to the reaper input shaft 38, and an input shaft side gear supported by the idler shaft 215 And a transmission shaft side gear. In the present embodiment, as shown in FIGS. 11 to 13, the amplification mechanism 200 has a first gear 211 and a fourth gear 214 as input shaft side gears, and a second gear 212 as a transmission shaft side gear. The third gear 213 is provided.

  As shown in FIG. 12, the first gear 211 is provided adjacent to the left side of the gear 120. The first gear 211 is supported rotatably relative to the reaper input shaft 38 via two bearings 216, 216 axially adjacent to each other. The first gear 211 coaxially supports the gear 120 in which the cutting input shaft 38 is penetrated so as to rotate integrally with the gear 120 with respect to the axial center of the cutting input shaft 38.

  The first gear 211 has a support cylindrical portion 211 a cylindrically protruding from the right side so as to be separated from the outer peripheral surface of the reaper input shaft 38 by a predetermined distance. The first gear 211 is fixed to the gear 120 by the fixing bolt 217 in a state where the support cylindrical portion 211 a is inserted into the inner circumferential hole 120 a of the gear 120 from the left side. The fixing bolt 217 penetrates a bolt hole 211 b formed in the first gear 211 from the left side and is screwed into the main body portion of the gear 120. Fixing portions by the fixing bolts 217 are provided at a plurality of locations (six locations in the present embodiment) at equal intervals around the axial center of the reaper input shaft 38. The outer diameters of the first gear 211 and the gear 120 are substantially the same.

  The idler shaft 215 is provided on the left side of the side portion 91 L of the feeder house 35 with the axial direction as the left-right direction at a position below the reaper input shaft 38. The idler shaft 215 has substantially the same length as the leftward projecting portion 38 a from the side surface portion 91 L of the reaper input shaft 38.

  The right end portion, which is one end side of the idler shaft 215, is rotatably supported via a bearing 218 in a lower shaft support hole 100b formed in the support bracket 100L. On the other hand, the left end which is the other end side of the idler shaft 215 is supported by the lower part of the erection support plate 220 which supports the left end of the reaper input shaft 38.

  The construction support plate 220 has, at its lower portion, a short cylindrical bearing support 220a whose left and right direction is the cylinder axial direction, and the end of the left side of the idler shaft 215 via the bearing 221 in the bearing support 220a. The part is rotatably supported. The installation support plate 220 is a plate-like member having a substantially chamfered rectangular outer shape whose longitudinal direction is the vertical direction in a side view, and supports the left end of the reaper input shaft 38 and the idler shaft 215. It is provided in a state of being bridged between the left end portions of these shafts.

  The idler shaft 215 is provided with a second gear 212 engaged with the first gear 211 at a position corresponding to the first gear 211 in the axial direction. The second gear 212 is fixed to the idler shaft 215 by welding or the like, and rotates integrally with the idler shaft 215. The second gear 212 is smaller in diameter than the first gear 211, and functions as a pinion with respect to the first gear 211.

  In the present embodiment, the number of teeth of the first gear 211 is 38, and the number of teeth of the second gear 212 is nineteen. That is, the gear ratio of the first gear 211 and the second gear 212 is 1/2, and the transmission of rotation from the first gear 211 to the second gear 212 has a speed increasing ratio of 2.

  A third gear 213 is provided to the left of the second gear 212 in the idler shaft 215. Similar to the second gear 212, the third gear 213 is fixed to the idler shaft 215 by welding or the like, and rotates integrally with the idler shaft 215. The third gear 213 is a gear larger in diameter than the second gear 212. In the present embodiment, the number of teeth of the third gear 213 is 38.

  A fourth gear 214 engaged with the third gear 213 is provided at a position corresponding to the third gear 213 in the axial direction of the reaper input shaft 38. The arrangement position of the third gear 213 is substantially adjacent to the left side of the first gear 211. The fourth gear 214 is cut by a parallel key 222 fitted in a key groove formed along the axial direction of the cutting input shaft 38 on each of the outer peripheral surface of the cutting input shaft 38 and the inner peripheral surface of the fourth gear 214. It is provided so as to be incapable of relative rotation with respect to the input shaft 38 and rotates integrally with the reaper input shaft 38. The fourth gear 214 is smaller in diameter than the third gear 213 and functions as a pinion with respect to the third gear 213.

  In the present embodiment, the number of teeth of the fourth gear 214 is 19 with respect to the third gear 213 having 38 teeth. That is, the gear ratio of the third gear 213 and the fourth gear 214 is 1/2, and the transmission of rotation from the third gear 213 to the fourth gear 214 has an acceleration ratio of 2.

  The left end of the reaper input shaft 38 is supported by the upper portion of the erection support plate 220 via a fourth gear 214. The fourth gear 214 has, on the left side of the main body where the teeth meshing with the third gear 213 are formed on the outer peripheral side, a cylindrical support cylindrical portion 214a in which the cutting input shaft 38 penetrates with the main body. On the other hand, the installation support plate 220 has a short cylindrical bearing support 220b in the upper portion thereof with the left and right direction being the cylinder axial direction, and the bearing 223 is interposed in the bearing support 220b in the fourth gear 214. A portion of the support cylindrical portion 214a is rotatably supported. That is, the left end of the reaper input shaft 38 is rotatably supported on the upper portion of the installation support plate 220 via the fourth gear 214 and the bearing 223.

  The reaper input shaft 38 has a left end where the male screw portion 38 b is formed protrudes to the left from the erection support plate 220. The projecting portion of the reaper input shaft 38 from the installation support plate 220 receives the threaded engagement of a nut 255 with the male screw portion 38b via a locking portion 224 formed of a washer, a snap ring, etc., which penetrates the reaper input shaft 38. It is supported.

  According to the amplification mechanism 200 as described above, as shown in FIGS. 12 and 13, in the operating state of the reverse rotation mechanism 110, the upward movement of the feeder 30 is received via the claw member 130, and it rotates in the reverse direction. The rotation of the gear 120 is the rotation of the first gear 211 which rotates relative to the reaper input shaft 38 integrally with the gear 120. The rotation of the first gear 211 is transmitted to the idler shaft 215 via the second gear 212 engaged therewith. Here, due to the speed increasing ratio of the first gear 211 and the second gear 212, the amount of rotation of the first gear 211 is increased and transmitted to the idler shaft 215. In the present embodiment, as described above, the speed increasing ratio between the first gear 211 and the second gear 212 is 2, and the amount of rotation of the first gear 211 is doubled and transmitted to the idler shaft 215.

  The rotation of the idler shaft 215 is transmitted to the reaper input shaft 38 via a third gear 213 that rotates integrally with the idler shaft 215 and a fourth gear 214 that meshes with the third gear 213. Here, due to the speed increasing ratio of the third gear 213 and the fourth gear 214, the amount of rotation of the third gear 213 is increased and transmitted to the fourth gear 214. Since the fourth gear 214 rotates integrally with the reaper input shaft 38, the amount of rotation of the fourth gear 214 directly becomes the amount of rotation of the reaper input shaft 38. In the present embodiment, as described above, the speed increasing ratio between the third gear 213 and the fourth gear 214 is 2, and the amount of rotation of the third gear 213 is doubled and the input of the reaper is via the fourth gear 214. It is transmitted to 38.

  As described above, according to the amplification mechanism 200, the rotation of the gear 120 integrated with the feeder 30 in the reverse rotation direction in the operating state of the reverse rotation mechanism 110 is the first gear 211 → the second gear 212 → the idler shaft 215 → the third The speed is increased by the flow of the gear 213 → the fourth gear 214 → the reaper input shaft 38, and is transmitted as the reverse rotation of the reaper input shaft 38. Further, in the present embodiment, the amount of rotation of the gear 120 is accelerated in two stages by the speed increasing ratio between the first gear 211 and the second gear 212 and the speed increasing ratio between the third gear 213 and the fourth gear 214. It is transmitted to the reaper input shaft 38 as a rotation amount of 4 times. The number of gears in the amplification mechanism 200, the number of teeth of each gear, the speed increase ratio between the gears, and the like are not particularly limited to the configuration of the present embodiment.

  Further, in the amplification mechanism 200, as described above, the erection support plate 220 supporting the left end of the reaper input shaft 38 and the idler shaft 215, as shown in FIG. And a support surface portion 220c formed by bending. That is, the installation support plate 220 is a portion that supports the left end of the reaper input shaft 38 and the idler shaft 215, and has a plate-like plate main body 220d whose thickness direction is the left-right direction And a plate-like support surface portion 220c, which has a direction, and has a substantially "L" shape in a plan view.

  The installation support plate 220 is provided so as to bring the support surface 220c into contact or substantially contact with the front side of the left column 105L on the side of the machine. In the installation support plate 220, the rear support surface portion 220c has a rear surface 220e as a contact surface to the front surface of the left support column 105L and serves as a support portion for the support column 105L.

  That is, in the operating state of the reversing mechanism 110, the reaper input shaft 38 receives the action from the front side to the rear via the claw member 130 and the gear 120 as the feeder 30 ascends. That is, the reaper input shaft 38 tries to escape rearward. Therefore, by using the support surface portion 220c of the erection support plate 220 supporting the left end portion of the reaper input shaft 38 as a support for the post 105L, the rearward movement of the reaper input shaft 38 is restricted, and the rear of the reaper input shaft 38 To the escape is prevented. Thereby, a stable engagement state can be obtained for the engagement of the claw member 130 with the gear 120.

  Further, in the amplification mechanism 200, the repelling input shaft 38 and the idler shaft 215 are generated by the reaction force of the meshing between the input shaft side gear supported by the reaper input shaft 38 and the transmission shaft side gear supported by the idler shaft 215. The action of the direction in which the axes of the two separate from each other occurs. Therefore, as shown in FIG. 12, a construction supporting plate 220 is provided between the cutting input shaft 38 and the idler shaft 215 in a bridging state, and the left end of each shaft is axially supported by the mounting supporting plate 220. It is done.

  According to such a configuration, the interaxial distance between the reaper input shaft 38 and the idler shaft 215 is held constant. As a result, separation between the input shaft side gear and the transmission shaft side gear constituting the amplification mechanism 200 is restricted, and a stable meshing state can be obtained for the meshing of these gears.

  As described above, according to the installation support plate 220, stable operation states can be obtained in the reverse rotation mechanism 110 and the amplification mechanism 200, and the reverse operation of the conveyor 36 by the reverse rotation mechanism 110 and the increase in the rotation by the amplification mechanism 200. It is possible to reliably obtain the speed transfer action.

  Then, the structure regarding operation of the reversing mechanism 110 in the combine 1 which concerns on this embodiment is demonstrated.

  The operation of the reversing mechanism 110 is operated by a predetermined operation tool via the operation wire 145 as described above. In this embodiment, a working clutch lever 23 (see FIGS. 14 and 15) for turning on and off the threshing clutch 57 and the reaper clutch 75 (see FIG. 4) provided in the operation unit 15 is an operating tool of the reversing mechanism 110. It is adopted.

  That is, in the combine 1 of the present embodiment, the operation / non-operation of the reversing mechanism 110 is operated by the operation of the work clutch lever 23 which is a work operation tool for operating the reaper portion 3 and the threshing portion 7. It is configured. Therefore, the other end side of the operation wire 145 is via a component of the link mechanism 300 provided between the claw member 130 and the working clutch lever 23 so that the reverse mechanism 110 is operated by the working clutch lever 23. It is connected to the work clutch lever 23. That is, the claw member 130 is interlocked and connected to the working clutch lever 23 by the link mechanism 300 including the operation wire 145.

  The operation structure and operation mode of the work clutch lever 23 as the operation tool of the reversing mechanism 110 will be described using FIGS. 14 and 15. As shown in FIG. 14, the working clutch lever 23 has a rod-like lever main body 23a having a predetermined shape, and a substantially spherical grip 23b provided on the upper end of the lever main body 23a.

  The work clutch lever 23 is provided so as to project upward from a lever guide portion 150 provided on a lever column 24 provided on the left side of the driver's seat 17. The lever guide portion 150 moves the lever main body portion 23a of the work clutch lever 23 through, and sets the plurality of operation positions corresponding to the predetermined operation content to the stop position along the predetermined operation movement path. Guide the movement. The lever main body portion 23a has a predetermined bending shape so as to extend upward from the lever column 24 in a tilting manner to the right side which is the driver's seat 17 side.

  The lever guide portion 150 has a guide opening 151 formed on the upper surface 24 a of the lever column 24 and a guide plate 152 provided below the guide opening 151.

  The guide opening 151 has a predetermined opening shape along the operation movement path of the working clutch lever 23. The guide plate 152 has a rectangular outer shape in plan view. The guide plate 152 has a plate opening smaller than the opening dimension of the guide opening 151 so as to be included in the opening range of the guide opening 151 in plan view, and having an opening shape along the opening shape of the guide opening 151 A portion 152a is formed. The plate opening 152 a is covered by an elastically deformable plate-like covering member 153. The covering member 153 has an opening through which the lever body 23 a of the working clutch lever 23 passes. The opening of the covering member 153 is formed of a slit-like portion along the movement path of the working clutch lever 23 and a wide portion such as a substantially circular shape at each operation position of the working clutch lever 23.

  The lever guide portion 150 is a path portion constituting an operation movement path of the work clutch lever 23, and a first movement path portion 161 extending in the left-right direction and a second portion extending forward from the right end portion of the first movement path portion 161. And a third movement path portion 163 extending rearward from the left end of the first movement path portion 161. The lever guide portion 150 is configured to have a substantially crank shape as a whole by these movement path portions. In FIG. 14, for convenience, each movement route portion is schematically shown as a hatched portion.

  Then, the working clutch lever 23 is a corner portion of the first movement path portion 161 and the third movement path portion 163 in the lever guide portion 150, and a corner of the first movement path portion 161 and the second movement path portion 162. The portion, the front end portion of the second movement path portion 162, and the rear end portion of the third movement path portion 163 are set as operation positions corresponding to predetermined operation contents. Specifically, it is as follows.

  The work clutch lever 23 has, as its operation position, the stop operation position P0 corresponding to the corner portion between the first movement path portion 161 and the third movement path portion 163, the first movement path portion 161, and the second The first work operation position P1 corresponding to the corner portion of the movement path portion 162, the second operation operation position P2 corresponding to the front end portion of the second movement path portion 162, and the rear end portion of the third movement path portion 163 There are four operation positions with the reverse operation position P3 corresponding to.

  The stop operation position P0 is an operation position in which the transmission of power to the reaper 3 and the threshing portion 7 is turned off and the reversing mechanism 110 is turned off. That is, in the state where the working clutch lever 23 is in the stop operation position P0 (see FIG. 15A), the reaper clutch 75 and the threshing clutch 57 (see FIG. 4) are in the OFF state, and the claw member 130 in the reversing mechanism 110. Is in the disengagement position, and the reaper input shaft 38 is disengaged from the feeder house 35. That is, the state in which the work clutch lever 23 is positioned at the stop operation position P0 is a so-called neutral state. In the present embodiment, on the surface of the lever column 24, in the vicinity of the stop operation position P0, the stop display unit 170 displaying the characters "OFF" is provided.

  The first work operation position P1 is a position moved by a predetermined amount in the right direction, which is the first direction, from the stop operation position P0, and is an operation position where transmission of power to the threshing portion 7 is in an ON state. That is, in a state where the work clutch lever 23 is in the first work operation position P1 (see FIG. 15 (b)), the reaper clutch 75 is OFF, the threshing clutch 57 is ON, and the reverse mechanism 110 is not operated. Yes, the threshing unit 7 is in operation. In the present embodiment, on the surface of the lever column 24, a threshing display unit 171 displaying the character “pickup” is provided in the vicinity of the first operation position P1.

  The second work operation position P2 is a position moved by a predetermined amount in the forward direction which is the third direction from the first work operation position P1, and the cutting operation is performed while maintaining the ON state of the transmission of power to the threshing portion 7 This is an operation position where transmission of power to the part 3 is in the on state. That is, in the state where the working clutch lever 23 is in the second work operation position P2 (see FIG. 15C), the reaper clutch 75 and the threshing clutch 57 are on, and the reverse mechanism 110 is in a non-operating state. 3 and the threshing part 7 are in operation. In the present embodiment, on the surface of the lever column 24, in the vicinity of the second operation position P2, a mowing display unit 172 displaying the character "mowing" is provided.

  The reverse operation position P3 is a position moved by a predetermined amount backward from the stop operation position P0 in the second direction different from the first direction, and is an operation position at which the reverse rotation mechanism 110 is in the operating state. That is, when the working clutch lever 23 is in the reverse rotation operation position P3 (see FIG. 15D), the reaper clutch 75 and the threshing clutch 57 are in the OFF state, and the claw member 130 is in the engagement position in the reverse rotation mechanism 110. The reaper input shaft 38 is engaged with the feeder house 35. In the present embodiment, on the surface of the lever column 24, in the vicinity of the reverse operation position P3, a reaping reverse display portion 173 displaying the character of "removing reverse" is provided.

  As described above, in the combine 1 according to the present embodiment, the work clutch lever 23 is a position moved a predetermined amount in at least the first direction from the stop operation position P0, and at least any one of the reaper 3 and the threshing part 7 A first operation position P1 and a second operation position P2 are provided as the operation positions where the transmission of power to the heel is in the on state. That is, the first operation position P1 is a position moved by a predetermined amount in the first direction (right direction) from the stop operation position P0, and at the operation position where power transmission to the threshing part 7 is in the on state The second operation position P2 is a position moved by a predetermined amount from the stop operation position P0 in the right direction and in the forward direction, and the operation operation position where power transmission to the threshing part 7 and the reaper 3 is in the ON state It is.

  In the present embodiment, the second direction, which is the moving operation direction from the stop operation position P0 of the work clutch lever 23 to the reverse operation position P3, is the movement from the first work operation position P1 to the second work operation position P2. It is opposite to the third direction which is the operation direction. That is, with respect to the operation direction of the work clutch lever 23, the third direction is the rear direction, and the rear direction which is the opposite direction is the second direction.

  Next, the link mechanism 300 including the operation wire 145 will be described with reference to FIG. 16 and FIG. As shown in FIGS. 16 and 17, the link mechanism 300 receives the engagement of the lever support pivot plate 310 as a first link member for supporting the base of the working clutch lever 23, and the lever support pivot plate 310. And a pivoting arm body 320 as a second link member that receives the connection of the other end of the operation wire 145.

  The lever support pivot plate 310 has a plate portion 311 which is a substantially mountain-shaped plate-like portion. The plate portion 311 is rotatably supported about the first rotation axis S1 along the left-right direction by the shaft support portion 312 in a direction in which the thickness direction is the left-right direction. The shaft support portion 312 is a portion having a cylindrical outer shape in which the left and right direction is the cylinder axis direction, and is provided in a penetrating manner with respect to the plate portion 311 at the upper portion (approximately mountain top) of the plate portion 311 . The bearing portion 312 is supported at a predetermined position with respect to a predetermined frame member disposed in the lever column 24. As described above, the lever support pivot plate 310 is provided rotatably around the first pivot axis S1 at a fixed position in the lever column 24.

  The lever support pivot plate 310 rotatably supports the base of the working clutch lever 23 on the plate portion 311. The rod-like lever main body portion 23a having a predetermined shape has a supported portion 23c bent toward the front in a portion extending downward from the lever guide portion 150. The supported portion 23 c is a portion whose axial direction (stretching direction) is substantially in the front-rear direction, and forms a base of the working clutch lever 23.

  The supported portion 23 c of the working clutch lever 23 is supported at the lower portion of the plate surface on the right side of the plate portion 311 so as to extend along the substantially mountain-shaped bottom side portion of the plate portion 311. The to-be-supported portion 23c is positioned at a predetermined position with the second rotational axis S2 coinciding with the central axis of the to-be-supported portion 23c by the annular or cylindrical axial support member 313 fixed to the plate portion 311. It is rotatably supported.

  Thus, the work clutch lever 23 can be pivoted back and forth about the first pivot axis S1 along the left and right direction by the lever support pivot plate 310, and the second time along the front and back direction in plan view It is supported so as to be rotatable in the left and right direction around the moving shaft S2. Then, in relation to the operation movement path of the work clutch lever 23 described above, the movement of the second movement path portion 162 and the third movement path portion 163 along the longitudinal direction causes the rotation of the work clutch lever 23 in the longitudinal direction. An operation is used, and a rotation operation in the left-right direction is used for the movement of the first movement path portion 161 along the left-right direction (see FIG. 14).

  The pivoting arm body 320 is directed rearward from a support shaft portion 323 pivoting about a third pivot shaft S3 along the left-right direction and an end portion on the right side which is one side of the support shaft portion 323 in the axial direction. It has a first arm 321 extended and a second arm 322 extended downward from the left end which is the other side of the support shaft portion 323 in the axial direction. The first arm 321 and the second arm 322 are integrally connected to each other through the support shaft portion 323, and form a substantially "L" shape in a side view as viewed in the axial direction of the third rotation shaft S3. 3) It integrally pivots around the pivot axis S3. The support shaft portion 323 is supported at a predetermined position with respect to a predetermined frame member disposed in the lever column 24. As described above, the pivoting arm body 320 is provided so as to be pivotable about the third pivoting axis S3 at a fixed position in the lever column 24.

  The first arm 321 is a longitudinal plate-like member, and is fixed to the right end of the support shaft portion 323 in a direction in which the thickness direction is the left-right direction. A long hole 321 a along the longitudinal direction of the first arm 321 is formed at the rear of the first arm 321. A rod-like engagement pin 314 protruding rightward from the lower front portion of the plate portion 311 passes through the long hole 321a. The engagement pin 314 is fixed to the plate portion 311 and rotates integrally with the plate portion 311.

  As described above, the pivoting arm body 320 is engaged with the lever supporting pivot plate 310 by causing the engagement pin 314 to penetrate the long hole 321 a of the first arm 321. Then, while the engaged state of the lever supporting and rotating plate 310 and the rotating arm body 320 is held by the engaging portion by the long hole 321a and the engaging pin 314, the plate portion 311 and the first arm 321 are rotated. Relative movement of the engagement pin 314 with respect to the first arm 321 is allowed. The long hole 321 a guides the direction of relative movement of the engagement pin 314 with respect to the first arm 321 in the longitudinal direction of the first arm 321.

  The second arm 322 is a longitudinal plate-like member, and is fixed to the left end of the support shaft 323 in a direction in which the thickness direction is the left-right direction. The other end of the operation wire 145 is connected to the middle of the second arm 322. At the other end of the operation wire 145, a rod-like connecting member 324 is provided. On the other hand, at the middle portion of the second arm 322, a rod-like connection pin 325 is provided so as to protrude leftward. The connecting pin 325 penetrates the tip of the connecting member 324. The connection member 324 is locked and supported by the connection pin 325, for example, by causing the tip of the connection pin 325 penetrating the connection member 324 to penetrate the locking pin. Thus, the other end of the operation wire 145 is connected to the second arm 322 of the pivoting arm body 320.

  In addition, the other end side of the operation wire 145 extends horizontally from the connecting end with respect to the second arm 322 substantially rearwardly via the support stay 332 to the wire support column 331 disposed in the lever column 24. It is supported. The support stay 332 is a bent plate-like member having a substantially "U" shape in a side view, and fixed by welding or the like to the wire support column 331 with the bottom side of the substantially "U" shape facing the front side. ing. At the other end of the covering tube 149 covering the operation wire 145, a wire support member 333 for allowing the operation wire 145 to penetrate together with the covering tube 149 is provided. The wire support member 333 is fixed to the support stay 332 in a manner of penetrating the front surface of the support stay 332.

  In this manner, the other end portion of the operation wire 145 defines the directivity of the operation force (pulling force) on the operation wire 145 and causes the operation force to stably act on the operation wire 145. It is horizontally supported along the direction. In detail, the forwardly extending portion of the operation wire 145 from the wire support member 333 is slightly inclined leftward and forward (see FIG. 17). By the connection structure of the operation wire 145 to the rotation arm body 320 as described above, the second arm 322 is moved to the front side by the rotation of the rotation arm body 320 about the third rotation axis S3, thereby the operation wire 145 will be pulled forward from the other end.

  Referring to FIG. 16, the operation clutch lever 23 is at an operation position other than the reverse operation position P3 such as the stop operation position P0, the first operation operation position P1, the second operation operation position P2, etc. (FIG. 14, FIG. (C), the link mechanism 300 (corresponding to the rotation restricting portion interlocking mechanism) applies a pulling action to the operation wire 145, and the reverse mechanism 110 (corresponding to the rotation restricting portion) is not It will be in operation state. On the other hand, when the work clutch lever 23 is moved from the stop operation position P0 to the reverse operation position P3 (see FIG. 14 and FIG. 15D), the rotation of the pivoting arm 320 about the third pivot axis S3. Along with the movement, the link mechanism 300 (corresponding to the rotation restricting portion interlocking mechanism) moves the second arm 322 to the rear side, releases the pulling action of the operation wire 145, and switches the reversing mechanism 110 to the operating state. . In this manner, when the operator or the like operates the working clutch lever 23 to the reverse operation position P3, the reverse mechanism 110 is switched to the operating state by the link mechanism 300, and the forward direction of the conveyor 36 (removing input shaft 38) is obtained. The rotation is regulated to set the conveyor 36 (the reaper input shaft 38) in a regulated state.

  When switching the reverse rotation mechanism 110 to the operating state (the reaper input shaft 38 is in the restricted state) and the work clutch lever 23 is positioned at the second work operation position P2, the operator etc. operates the work clutch lever 23 at the second work operation position P2. To the reverse operation position P3. In this case, if the operation time of the work clutch lever 23 becomes short, such as when the operator etc. operates the work clutch lever 23 all at once from the second work operation position P2 to the reverse operation position P3, the following problems may occur. is there.

  When the work clutch lever 23 is positioned at the second work operation position P2, the mowing part 3 and the threshing part 7 are in the operating state, so the conveyor 36 of the feeder 30 in the mowing part 3 is in the forward direction (see arrow B2 in FIG. 6). ) To rotate. On the other hand, when the working clutch lever 23 is positioned at the reverse rotation operation position P3, the reverse rotation mechanism 110 is in the operating state, so as shown in FIGS. 9 and 10, the gear 120 on the reaper input shaft 38 side and the feeder house 35 side The claw members 130 are engaged with each other, and the rotation of the conveyor 36 (the reaper input shaft 38) in the forward direction is restricted. Therefore, when the operation time of the work clutch lever 23 becomes short, the reaper input shaft 38 may be still rotating due to inertia or the like, and the claw member 130 is engaged with the gear 120 rotating integrally with the reaper input shaft 38. As a result, the gear 120, the claw member 130, the first to fourth gears 211 to 214, and the like may be damaged.

  Therefore, the combine 1 according to the present embodiment includes a check control unit 500 that checks that the conveyor 36 is in the restriction state until a predetermined condition is satisfied. Here, the predetermined condition is a condition under which the rotation of the reaper input shaft 38 is stopped and the rotation of the conveyor 36 in the forward rotation direction is stopped when the condition is satisfied. The check control unit 500 will be described using FIGS. 18 to 20. FIG. Incidentally, in FIG. 18 to FIG. 20, constituent members such as the link mechanism 300 and the check control portion 500 are shown in a right side view, the right side in the drawing is the front side, and the left side in the drawing is the rear side.

  The check control unit 500 is configured to be switchable between a check control state for checking that the conveyor 36 is in the control state and a check release state for releasing the check control state while utilizing the components of the link mechanism 300 as it is. ing. As described above, since the check control unit 500 utilizes the constituent members such as the lever support rotation plate 310 and the rotation arm body 320 shown in FIG. 16 as it is, in FIGS. The detailed description of the configurations of the lever support pivot plate 310, the pivot arm body 320 and the like will be omitted. By the way, in FIG. 18 to FIG. 20, in order to make the configuration of the check portion 500 intelligible, switches such as the threshing switch 401 and supporting components are omitted. Further, FIGS. 18 to 20 show a state where the periphery of the supported portion 23c of the work clutch lever 23 is covered with the cylindrical portion 23d.

  As shown in FIG. 18, the combine 1 is provided with a parking brake mechanism 600 (corresponding to a machine movement restricting portion) for restricting the movement of the traveling machine body 2, and the check control portion 500 operates when the parking brake mechanism 600 is in operation. In conjunction with switching to the non-operating state, switching to the check state and the non-check state is configured.

  First, the parking brake mechanism 600 will be described. The parking brake mechanism 600 restricts the movement of the traveling airframe 2 by being activated, and releases the state of restricting the movement of the traveling airframe 2 by being deactivated. The parking brake mechanism 600 has a parking brake pedal 601 that can be depressed by an operator or the like, and a parking brake that can be switched between an operating state and a non-operating state according to the operation position of the parking brake pedal 601.

  Although not shown, the parking brake is provided, for example, in a transmission 65 (see FIG. 4) that outputs a driving force for driving the drive sprocket 5a of the crawler unit 5 to rotate. The parking brake is configured to be switchable to an operating state that regulates the movement of the traveling vehicle 2 by regulating the output of the driving force from the transmission 65 by regulating the rotation of the rotation shaft on the output side of the transmission 65 There is. Incidentally, the parking brake is not limited to the one provided in the transmission 65, as long as it restricts the rotational drive of the drive sprocket 5a of the crawler unit 5, and various other parking brakes can be applied.

  The parking brake pedal 601 is disposed on the right side of the front portion of the lever column 24. The parking brake pedal 601 has a parking brake mechanism 600 in a non-operating position Q1 (see FIG. 18) and a parking position Q2 (see FIGS. 19 and 20) in a parking state. 5 is rotatably provided centering on a rotation axis S5.

  The parking brake pedal 601 is urged back to the inoperative position Q1 by the urging force of an elastic body 609 described later. When the parking brake pedal 601 is located at the inoperative position Q1, the lower end portion of the parking brake arm 607 described later abuts against a stopper member (not shown) so that the parking brake 601 does not rise beyond the inoperative position Q1. Configured On the other hand, in a state where the parking brake pedal 601 is rotated to the operating position Q2, as shown by the alternate long and short dash line in FIGS. 19 and 20, the engaging pin 605 is engaged with the engaging groove portion 604 formed in the rotating portion 603. By engagement, the parking brake pedal 601 can be held at the operating position Q2. The engagement pin 605 is provided so as to be able to extend and retract in the left and right direction from the lever column 24 and the like to the parking brake pedal 601 side, and is operated by moving the engagement pin 605 out and back by human operation such as an operator. The engagement pin 605 can be engaged with the engagement groove portion 604 of the parking brake pedal 601 rotated to the position Q2.

  The parking brake pedal 601 has a plate shape with the lateral direction as the plate width direction, and the proximal end is laterally extended by the rod supporting portion 606 extending from the proximal end portion to the distal end portion. And a pivoting portion 603 rotatably supported about a fifth pivoting axis S5 along the axis. A step-in portion 602 is fixed to the tip of the pivoting portion 603. The shaft support portion 606 is a cylindrical shape having an axial center direction in the left and right direction, and is rotatably supported at a predetermined position with respect to a predetermined frame member provided in the lever column 24. Thus, the parking brake pedal 601 and the pivot portion 606 integrally pivot around the fifth pivot axis S5.

  The parking brake mechanism 600 has a parking brake arm 607 pivoted about a fifth pivot axis S5 to link the operation of the parking brake pedal 601 and the operation of the parking brake provided in the transmission 65, and parking A parking brake operation unit 608 is operated to switch the parking brake between the operating state and the non-operating state in conjunction with the rotation of the brake arm 607.

  The parking brake arm 607 is fixed to the pivot portion 606 and is formed in a plate shape extending forward, and integrally pivots with the pivot portion 606 and the parking brake pedal 601 about the fifth pivot axis S5. Although not shown, the parking brake operation unit 608 incorporates an operation wire, for example, and operates the parking brake by operating the operation wire in conjunction with the rotation of the parking brake arm 607. It is configured to be able to switch to the non-operating state.

  The tip of the parking brake arm 607 is connected to the parking brake operating unit 608, and the parking brake operating unit 608 is operated to move upward and downward by turning the parking brake arm 607. It is configured to be switchable to the state. When the parking brake operation unit 608 is moved upward, the parking brake is inactivated, and when the parking brake operation unit 608 is moved downward, the parking brake is operated. Is activated. An elastic body (for example, a spring) 609 is provided to urge the parking brake operation unit 608 upward, and the parking brake operation unit 608 is moved upward by the urging force of the elastic body 609. It is energized. One end of the elastic body 609 is hooked on a predetermined frame member provided in the lever column 24 and the other end is hooked on the tip of the parking brake operation unit 608.

  As shown in FIG. 18, when the parking brake pedal 601 is positioned at the non-operating position Q1 in the inclined posture in which the parking brake pedal 601 is positioned on the upper side toward the front side, the parking brake arm rotates integrally with the parking brake pedal 601. By 607, the parking brake operation unit 608 is moved upward, the parking brake of the transmission 65 is switched to the non-operating state, and the parking brake mechanism 600 is switched to the non-operating state.

  When the parking brake pedal 601 is depressed by the operator or the like, as shown in FIGS. 19 and 20, the parking brake pedal 601 is pivoted about the fifth pivot axis S5 and is forward of the inclined attitude of FIG. The parking brake operating portion 608 is switched to the lower side by the parking brake arm 607 which is located at the operating position Q2 where the side has moved downward and is rotated integrally with the parking brake pedal 601, The parking brake of the transmission 65 is switched to the operating state, and the parking brake mechanism 600 is switched to the operating state.

  The check control unit 500 holds the movement of the link mechanism 300 until the predetermined condition is satisfied and holds the movement of the work clutch lever 23 to the reverse operation position P3, thereby operating the reverse mechanism 110 (the conveyor 36 is in the restricted state). It is configured to be able to prevent becoming The check control unit 500 can move in conjunction with the rotation of the parking brake pedal 601 in the parking brake mechanism 600. As shown in FIG. 18, when the parking brake pedal 601 is located at the inoperative position Q1, the check control portion 500 is switched to the stationary state, and as shown in FIG. 19, the parking brake pedal 601 is located at the operative position Q2. In this case, the check control unit 500 is switched to the check release state.

  The check control portion 500 is fixed to the first link 501 in an upward and downward inclined posture extending toward the rear side (left side in FIGS. 18 to 20) toward the upper side, and fixed to the pivot portion 606 to the front side (right side in FIGS. And a second link 502 extending to the The 1st link 501 and the 2nd link 502 are formed in plate shape which makes the direction of order the board thickness direction. The lower end portion of the first link 501 and one end portion of the second link 502 are pivotally coupled about the first pivot axis R1 along the left-right direction. Thus, the second link 502 integrally pivots with the parking brake pedal 601 and the pivot portion 606 about the fifth pivot axis S5, and the first link 501 is integral with the parking brake pedal 601 and the pivot portion 606. The second link 502 pivots about the first pivot R1 with respect to the second link 502 that pivots. Therefore, in conjunction with the movement of the parking brake pedal 601, the first link 501 and the second link 502 are configured to be movable.

  Here, the parking brake pedal 601, the parking brake arm 607, and the second link 502 are fixed to the pivot portion 606, but the parking brake pedal 601, the second link 502, the parking brake are from the right side in the left-right direction. The arms 607 are arranged in order. As a result, the parking brake pedal 601, the second link 502, and the parking brake arm 607 are integrally pivoted by pivotal movement of the pivot portion 606 about the fifth pivot axis S5.

  At the upper end portion of the first link 501, a sloped long hole portion 503 is formed extending upward and backward. An engagement pin 314 protruding from the plate portion 311 is engaged with the long hole portion 503 of the first link 501 in a penetrating state. Further, the first link 501 is formed with a sloped second contact portion 505 extending to the side projecting forward from near the lower end portion of the formation portion of the long hole portion 503, and the projection side of the contact portion 505 A downwardly sloping first contact portion 504 is formed which extends forward from the end toward the lower side. The first contact portion 504 of the first link 501, as shown in FIG. 18, when the parking brake pedal 601 is positioned at the non-operating position Q1, the pivoting arm 320 as the working clutch lever 23 pivots. The support shaft portion 323 of the (first arm 321 and the second arm 322) is provided so as to be abuttable. As shown in FIG. 20, the second contact portion 505 of the first link 501 switches the parking brake pedal 601 from the operating position Q2 to the non-operating position Q1 when the working clutch lever 23 is positioned at the reverse operation position P3. As it is intended, the support shaft portion 323 of the pivoting arm body 320 (the first arm 321 and the second arm 322) is provided so as to be abuttable.

  As shown in FIG. 18, when the working clutch lever 23 is at the stop operation position P0 (see FIG. 14) and the parking brake pedal 601 is at the non-operation position Q1, the engagement pin 314 is the first link 501. And the first contact portion 504 of the first link 501 is rearward with respect to the support shaft portion 323 of the pivot arm 320 (the first arm 321 and the second arm 322). Abutment is possible from the lower side. Thereby, even if the first link 501 is to move forward and upward, the forward and upward movement of the first link 501 is restrained by the contact of the first contact portion 504 with the support shaft portion 323. At this time, if the operator or the like tries to move the working clutch lever 23 to the reverse operation position P3, the plate portion 311 rotates about the first pivot axis S1 in the left rotation direction (counterclockwise direction) in a right side view. Do. However, since the forward upward movement of the first link 501 is restrained, the engagement between the engagement pin 314 of the plate portion 311 and the long hole portion 503 of the first link 501 causes the first plate portion 311 to receive the first movement. The rotation in the left rotation direction (counterclockwise direction) is restrained in a right side view centering on the rotation axis S1, and the movement of the working clutch lever 23 to the reverse rotation operation position P3 is restrained. Thus, the check control unit 500 checks the movement of the link mechanism 300 (plate unit 311) to check the movement of the working clutch lever 23 to the reverse operation position P3, whereby the reverse mechanism 110 is in the operating state (the conveyor 36). Is in a state of control).

  By the way, as shown in FIG. 18, although the movement of the first link 501 to the upper front side is restrained by the contact of the first contact portion 504 with the support shaft portion 323, the rear lower side of the first link 501 Movement to the side is not restricted. Therefore, in the state shown in FIG. 18, the movement of the work clutch lever 23 from the stop operation position P0 to the first work operation position P1 and the second work operation position P2 is permitted. Thus, when the parking brake pedal 601 is in the non-operation position Q1, the work clutch lever 23 is operated to the first work operation position P1 or the second work operation position without receiving the check by the check unit 500. The threshing part 7 and the reaper 3 can be operated.

  In the state shown in FIG. 18, when the operator or the like depresses the parking brake pedal 601, as shown in FIG. 19, the parking brake pedal 601 moves to the operating position Q2 and interlocks with the movement of the parking brake pedal 601. The 2 link 502 and the first link 501 move, and the engagement pin 314 is positioned from the middle to the top of the long hole portion 503 of the first link 501, and the first contact portion 504 of the first link 501 is rotated. The arm body 320 (the first arm 321 and the second arm 322) is moved downward from the support shaft portion 323 of the arm body 320 (the first arm 321 and the second arm 322). As a result, the forward and upward movement of the first link 501 is not restricted. Therefore, the plate portion 311 is allowed to rotate in the left rotation direction (counterclockwise direction) around the first rotation axis S1 in the right side view, and the operator etc. operate the working clutch lever 23 to the reverse operation position P3. As a result, the reversing mechanism 110 can be put into operation (the conveyor 36 is in a restricted state). Thus, the check control unit 500 is switched to the check release state on the assumption that the predetermined condition is satisfied along with the movement of the parking brake pedal 601 to the operating position Q2, and the predetermined condition is that the parking brake mechanism 600 is operated. It is something that includes being in the state.

  As described above, when the parking brake mechanism 600 is switched to the inoperative state by the working clutch lever 23 as shown in FIG. 18, the check control unit 500 regulates the movement of the working clutch lever 23 to thereby prevent the link mechanism 300 from moving. By restricting the operation of the reverse rotation mechanism 110 due to the above, the restriction of the conveyor 36 (the reaper input shaft 38) is restricted. In addition, as shown in FIG. 19, the check control unit 500 allows the movement of the working clutch lever 23 in conjunction with the parking brake mechanism 600 being switched to the operating state by the parking brake pedal 601, thereby causing the link mechanism 300 to rotate in reverse. 110 can be actuated to put the conveyor 36 (the reaper input shaft 38) in a restricted state. Thus, in configuring the check control unit 500 and the link mechanism 300, the movement of the working clutch lever 23 for operating the connection / disconnection of power to the reaper 3 and the threshing unit 7 including the conveyor 36 etc. and the parking brake mechanism 600 are operated. By utilizing the movement of the parking brake pedal 601 operated to the state and the non-operation state, the configuration is simplified without providing another operation unit.

  In the state shown in FIG. 19, when the operator etc. operate the working clutch lever 23 to the reverse operation position P3, as shown in FIG. 20, the plate portion 311 rotates leftward in the right side view centering on the first pivot shaft S1. (Counterclockwise), the engagement pin 314 moves to the upper end of the long hole portion 503 of the first link 501, and moves the first link 501 forward and upward around the first pivot R1. The second contact portion 505 of the first link 501 faces the support shaft portion 323 of the pivoting arm body 320 (the first arm 321 and the second arm 322) from the lower front side. As a result, even if the first link 501 tries to move rearward and upward, the upward and rearward movement of the first link 501 is restricted by the contact of the second contact portion 505 with the support shaft portion 323. At this time, when the operator or the like tries to operate the parking brake pedal 601 to the inoperative position Q1, the first link 501 tends to move rearward and upward via the second link 502. However, since the movement of the first link 501 to the rear upper side is restricted, the movement of the parking brake pedal 601 to the inoperative position Q1 is restricted. As described above, the pivoting arm body 320 of the link mechanism 300 restricts the movement of the first link 501 of the check unit 500, thereby making it impossible to switch the parking brake mechanism 600 from the operating state to the non-operating state.

  In the state shown in FIG. 20, when the operator or the like operates the working clutch lever 23 to the stop operation position P0, as shown in FIG. 19, the plate portion 311 rotates clockwise about the first pivot shaft S1 in a right side view. (Clockwise), the engagement pin 314 moves to the middle of the long hole portion 503 of the first link 501, and moves the first link 501 rearward and downward around the first pivot R1; The second contact portion 505 of the first link 501 moves to a position where it does not face the support shaft portion 323 of the pivot arm 320 (the first arm 321 and the second arm 322). Accordingly, the movement of the first link 501 to the rear upper side is not restricted, and the operator or the like can operate the parking brake pedal 601 to the inoperative position. Here, the inclination angle of the second contact portion 505 can be changed as appropriate. For example, the movement of the first link 501 to the rear and lower side can be performed by increasing the inclination angle of the front lowering. Makes it easy to do

  Alternatively, the second contact portion 505 has a plane substantially perpendicular to the moving direction of the first link 501 when the parking brake pedal 601 is switched between the inoperative position Q1 and the operative position Q2. It is also good. According to this configuration, when the parking brake pedal 601 is to be switched from the operating position Q2 to the non-operating position Q1 when the second contact portion 505 is in contact with the support shaft portion 323, the first link 501 The contact between the support shaft 323 and the surface perpendicular to the direction of movement of the vehicle allows the switching of the parking brake mechanism 600 from the operating state to the non-operating state to be made more reliably impossible.

  The work clutch lever 23 for operating the link mechanism 300 is provided with a plurality of switches operated by the operation of a predetermined member interlocked with the operation of the work clutch lever 23. The plurality of switches include a threshing switch 401, a reaper switch 402, and a reverse switch 403. These switches function as detection means for detecting the operation position of the working clutch lever 23, and are connected to a controller 400 as a control unit provided in the combine 1 as shown in FIG. In addition, an engine start permission switch 700 for detecting the operation position of the parking brake pedal 601 is provided, and the engine start permission switch 700 is also connected to the controller 400.

  The controller 400 connects various functional units such as a central processing unit (CPU) that executes various arithmetic processing and control, a ROM (read only memory) as a storage unit, a random access memory (RAM), and an input / output interface via a bus or the like. It has a configuration that The CPU performs arithmetic processing in accordance with various programs stored in the ROM or the like. The controller 400 receives detection signals from the threshing switch 401, the reaper switch 402, and the reverse switch 403, and detection signals from various sensors included in the combine 1, and generates control signals based on these input signals.

  A threshing clutch 57 is connected to the controller 400 via a threshing clutch actuator (not shown). The controller 400 controls the operation of the threshing clutch 57 based on the detection signal from the threshing switch 401 through the operation control of the threshing clutch actuator. In addition, a reaper clutch 75 is connected to the controller 400 via a reaper clutch actuator (not shown). The controller 400 controls the operation of the reaper clutch 75 based on the detection signal from the reaper switch 402 via the operation control of the reaper clutch actuator. Further, the detection signal by the reverse rotation switch 403 and the detection signal by the engine start permission switch 700 are used for the start / stop control of the engine 25 to be described later which is performed by the controller 400.

  The threshing switch 401 is a detection device for detecting that the work clutch lever 23 is in a position from the first work operation position P1 to the second work operation position P2 which is a position corresponding to the threshing “on”. Specifically, the threshing switch 401 is brought into the detection ON state by the work clutch lever 23 moving from the stop operation position P0 to the first work operation position P1 (see FIG. 14).

  As shown in FIGS. 16 and 17, the threshing switch 401 is a push switch having a push button 401a, and is turned on when the push button 401a is pressed. The threshing switch 401 is on the left side of the longitudinal stretching frame 341 disposed along the longitudinal direction at the position of the left side of the working clutch lever 23 in plan view in the lever column 24 with the push button 401a side as the rear side. It is fixedly supported at a predetermined position by a fixing tool such as a bolt via a support plate 342.

  On the other hand, on the rear side of the working clutch lever 23, a pressing member 350 is provided which presses the push button 401a in conjunction with the moving operation of the working clutch lever 23. The pressing member 350 has a cylindrical shaft support 351 whose vertical direction is the cylinder axis direction, an engagement arm piece 352 provided on the front side of the shaft support 351 and engaged with the working clutch lever 23, and the left from the shaft support 351 And a pressing arm piece 353 that extends toward the pressing force acting on the push button 401a.

  The pressing member 350 coaxially supports the support portion 351 with respect to a support column 354 (see FIG. 16) provided on the rear side of the working clutch lever 23 in the lever column 24, and the cylindrical support portion 351. It is provided to rotate about a fourth rotation axis S4 along the vertical direction that coincides with the central axis of the lens. The support column 354 is fixed on the rear side by welding or the like with respect to the horizontal frame 344 which is provided between the front and rear extension frame 341 and the right front and rear extension frame 343 disposed on the right side in parallel in the lever column 24. It is set up. The engaging arm piece 352 and the pressing arm piece 353 constitute an integral pressing member 350 together with the support portion 351, and rotate around the fourth rotation axis S4.

  The engagement arm piece 352 is a plate-like portion whose thickness direction is in the vertical direction, and has a concave portion 352a which is branched on the front side into a bifurcated shape and on the front side as the open side. The pressing member 350 engages with the working clutch lever 23 by positioning the lever main body 23 a in the recess 352 a of the engagement arm piece 352.

  The pressing arm piece 353 is a plate-like portion whose thickness direction is substantially in the front-rear direction, and the tip end side is provided on the front side of the push button 401 a. The plate surface 353a on the front side of the pressing arm piece 353 serves as a pressing surface, and presses the push button 401a.

  With such a configuration, leftward and rightward rotation of the working clutch lever 23 about the second rotation shaft S2 is centered on the fourth rotation shaft S4 of the pressing member 350 via the engagement arm piece 352. It is transmitted as rotation in the left and right direction. The on / off of the threshing switch 401 is switched by the movement of the pressing arm piece 353 in the front-rear direction by the rotation of the pressing member 350. That is, by moving the work clutch lever 23 from the stop operation position P0 toward the first work operation position P1 in the right direction, the pressing member 350 is rotated in the right rotation direction (clockwise direction) in plan view. Along with this, the pressing arm piece 353 moves forward and presses the push button 401a, and the threshing switch 401 is turned ON. The ON state of the threshing switch 401 is also maintained by moving the work clutch lever 23 from the first work operation position P1 to the second work operation position P2. On the other hand, by returning the working clutch lever 23 from the first work operation position P1 to the stop operation position P0, the pressing action of the pressing arm piece 353 against the push button 401a is released with the rotation of the pressing member 350, and the threshing switch 401 Is in the OFF state.

  The reaper switch 402 is a detection device for detecting that the work clutch lever 23 is at a second work operation position P2, which is a position corresponding to reaper "on". Specifically, the reaper switch 402 detects that the work clutch lever 23 has moved from the first work operation position P1 to the second work operation position P2.

  As shown in FIG. 16, the reaper switch 402 is a lever switch having a pivoting lever 402a pivoting about a predetermined pivoting axis, and the pivoting lever 402a pivots by a predetermined amount from the OFF state. It will be in the state of ON. The reaper switch 402 projects the pivoting lever 402a upward and is oriented such that the pivoting axis of the pivoting lever 402a is in the left-right direction, and is horizontal at a position below the lever support pivoting plate 310 in the lever column 24. The switch support stay 345 is fixedly supported at a predetermined position by a fixing tool such as a bolt.

  On the other hand, the plate portion 311 is provided with a first lever operation arm 371. The first lever operating arm 371 is a rod-like portion bent in an L-shape, fixed to the front end of the plate portion 311 by welding or the like and extending downward, and at the extending end, leftward It has a horizontal axis portion 371a bent toward the left and right along the rod axis direction. The first lever operating arm 371 positions the lateral shaft portion 371 a on the front side of the turning lever 402 a of the reaper switch 402.

  With such a configuration, reaping is performed by forward and backward movement of the first lever operating arm 371 associated with pivoting of the lever supporting pivot plate 310 by pivoting of the working clutch lever 23 in the back and forth direction about the first pivot axis S1. The switch 402 is switched ON / OFF. That is, by moving the work clutch lever 23 forward from the first work operation position P1 to the second work operation position P2, the plate portion 311 is rotated in the right rotation direction (clockwise direction) in a right side view. Along with this, the horizontal shaft portion 371a of the first lever operation arm 371 moves rearward and presses the pivoting lever 402a to pivot rearward, and the reaper switch 402 is turned ON. On the other hand, by returning the work clutch lever 23 from the second work operation position P2 to the first work operation position P1, the first lever operation arm 371 presses the rotation lever 402a with the rotation of the lever support rotation plate 310. The action is released, and the reaper switch 402 is turned off.

  The reverse rotation switch 403 is a detection device for detecting that the working clutch lever 23 is at the reverse rotation operation position P3 which is a position corresponding to the cutting reverse rotation "on". Specifically, the reverse rotation switch 403 detects that the work clutch lever 23 has moved from the stop operation position P0 to the reverse operation position P3.

  Similar to the reaper switch 402, the reverse rotation switch 403 is a lever switch having a rotation lever 403a that rotates about a predetermined rotation axis, and is turned ON by rotating the rotation lever 403a by a predetermined amount from the OFF state. It will be in the state of The reverse rotation switch 403 is a fixing tool such as a bolt or the like on a predetermined support member provided in the lever column 24 so that the rotation lever 403 a protrudes upward and the rotation axis direction of the rotation lever 403 a is right and left. Fixedly supported at a predetermined position.

  On the other hand, the second arm 322 is provided with a second lever operation arm 372. The second lever operating arm 372 is a rod-like portion bent in an L-shape, fixed by welding or the like to the lower side of a left-side bending surface 322 a provided at the lower end of the second arm 322 and extending downward. It has a lateral axis portion 372a bent at the extension end and bent in the right direction along the lateral direction of the rod axis direction. The second lever operating arm 372 positions the lateral shaft portion 372 a on the front side of the pivot lever 403 a of the reverse rotation switch 403.

  With such a configuration, the second lever operation associated with the pivoting of the pivoting arm body 320 via the lever support pivoting plate 310 by the pivoting of the working clutch lever 23 in the front-rear direction about the first pivoting axis S1. By the forward and backward movement of the arm 372, the reverse switch 403 is switched ON / OFF. That is, by moving the working clutch lever 23 rearward from the stop operation position P0 to the reverse operation position P3, the plate portion 311 is rotated in the left rotation direction (counterclockwise direction) in the right side view, Interlockingly with it, the pivoting arm body 320 pivots in the right rotation direction in a right side view, and along with this, the horizontal shaft portion 372a of the second lever operating arm 372 moves rearward and presses the pivoting lever 403a Then, it is rotated backward, and the reverse rotation switch 403 is turned on. On the other hand, by returning the working clutch lever 23 from the reverse rotation operation position P3 to the stop operation position P0, the lever support rotation plate 310 and the rotation arm body 320 are rotated together with the rotation lever 403a by the second lever operation arm 372 Is released, and the reverse rotation switch 403 is turned off.

  Further, as shown in FIGS. 19 and 20, an engine start permission switch 700 is provided to detect that the parking brake pedal 601 is in the operating position Q2. Engine start permission switch 700 detects that the parking brake pedal 601 has moved from the inoperative position Q1 to the operative position Q2.

  The engine start permission switch 700 is a push switch having a push button 701a as in the threshing switch 401, as shown in FIG. 18, and is turned on when the push button 701a is pressed. The engine start permission switch 700 is fixedly supported at a predetermined position by a predetermined support member provided in the lever column 24 in a direction in which the push button 701a side is the lower side.

  On the other hand, on the rear side of the parking brake arm 607, the push button is interlocked with the pivoting in the right rotation direction (clockwise direction) in a right side view centering on the fifth pivot axis S5 by the parking brake arm 607 A pressing member 610 is provided which presses against 701a.

  With such a configuration, when the parking brake pedal 601 pivots about the fifth pivot axis S5, the parking brake arm 607 pivots about the fifth pivot axis S5 in conjunction with this. The pivoting of the parking brake arm 607 moves the pressing member 610 in the vertical direction, and the ON / OFF of the engine start permission switch 700 is switched. That is, by depressing the parking brake pedal 601 from the inoperative position Q1 (see FIG. 18) to the operative position Q2 (see FIG. 19), the pressing member 350 moves upward and presses the push button 701a. The engine start permission switch 700 is turned on.

  One example of the operation mode of the combine 1 having the above-described configuration will be described with reference to FIGS. 15, 18, 19, 20, 22, and 23. FIG.

  First, the neutral state in which the work clutch lever 23 is at the stop operation position P0 will be described. In this state, as shown in FIGS. 15 (a) and 22 (b), the working clutch lever 23 is positioned at the neutral position in the front-rear direction and at the left position in the left-right direction. Both 402 and the reverse switch 403 are in the OFF state. That is, in the neutral state, the pressing arm piece 353 does not act on the threshing switch 401, the first lever operating arm 371 does not act on the reaper switch 402, and the second lever operating arm 372 does not act on the reverse switch 403 ing.

  Further, in the neutral state, as shown in FIG. 23B, the reversing mechanism 110 is in the non-operating state, and the claw member 130 is in the non-engaging position. When the claw member 130 is in the non-engagement position, the pivoting arm body in the predetermined pivoting position via the lever support pivoting plate 310 corresponding to the work clutch lever 23 held in the neutral position in the front-rear direction It is held by the pulling action of the manipulation wire 145 against the biasing action of the spring 140 according to 320. The state in which the working clutch lever 23 is positioned at each operation position is held by an appropriate structure such as a connection supporting structure of each member in the link mechanism 300 or a predetermined holding structure provided separately.

  From the neutral state, at the time of work start, as shown in FIG. 15 (b), the work clutch lever 23 is moved rightward from the stop operation position P0 toward the first work operation position P1 (see arrow X1) . Thereby, the pressing member 350 engaged with the working clutch lever 23 pivots in the right rotation direction in plan view centering on the fourth pivot shaft S4 (see FIG. 17, arrow M1), and the threshing switch is performed by the pressing arm piece 353 When the push button 401 a 401 is pressed, the threshing switch 401 is turned on. Thereby, it is detected that the work clutch lever 23 is at the first work operation position P1.

  When a detection signal from the threshing switch 401 is input to the controller 400, the controller 400 sends a control signal to turn on the threshing clutch 57 to the threshing clutch actuator. As a result, the threshing clutch 57 is turned ON, the threshing unit 7 starts operating, and the threshing drum 41 and the like begin to rotate.

  Further, when the work clutch lever 23 is in the first work operation position P1, the reverse rotation mechanism 110 is in the non-operation state as in the case of the neutral state (see FIG. 23 (b)). This is based on the fact that the work clutch lever 23 is in the neutral position in the front-rear direction even when the work clutch lever 23 is in either the stop operation position P0 or the first work operation position P1.

  Next, as shown in FIG. 15C, the work clutch lever 23 is moved forward from the first work operation position P1 to the second work operation position P2 (see arrow X2). As a result, the lever support pivot plate 310 pivots about the first pivot shaft S1 in the right rotation direction in a right side view (see FIG. 22 (c), arrow M2), and the first lever operation arm 371 cuts off The pivoting lever 402a of the switch 402 is pushed and pivoted, and the reaper switch 402 is turned on. Thus, it is detected that the work clutch lever 23 is at the second work operation position P2. Here, since the position in the left-right direction of the work clutch lever 23 is constant between the first work operation position P1 and the second work operation position P2, the rotation of the pressing member 350 for setting the threshing switch 401 to the ON state is performed. In the state where the movement position is held, the forward movement of the working clutch lever 23 is permitted by the recess 352 a of the engagement arm piece 352.

  When a detection signal from the reaper switch 402 is input to the controller 400, the controller 400 sends a control signal to put the reaper clutch 75 into the "on" state to the reaper clutch actuator. As a result, in a state where the threshing unit 7 is in operation, the reaper clutch 75 is turned on, the reaper 3 starts operating, and the conveyor 36 of the feeder 30, the scraping auger 37, and the like starts to rotate. As a result, the combine 1 is in the working state, and the mowing operation by the reaper 3 and the threshing operation by the threshing unit 7 are performed.

  Then, when clogging of cereal grains occurs in the feeder 30 during the work by the combine 1, as shown in FIG. 15 (d), the work clutch lever 23 moves from the second work operation position P2 to the reverse operation position P3. Move to As a result, the operation of the reaper 3 and the threshing unit 7 is stopped, and the reversing mechanism 110 is activated.

  Here, the work clutch lever 23 includes the second movement path portion 162, the first movement path portion 161, and the third movement path portion 163 so as to pass through the first operation operation position P1 and the stop operation position P0. Move along a crank-like path. Specifically, the working clutch lever 23 moves from the working state of the combine 1 to the reverse operation position P3 through the following three steps.

  That is, in the first step, the lever support rotation plate 310 is rotated in the left rotation direction in a right side view to release the action of the first lever operation arm 371 on the reaper switch 402, and the reaper switch 402 is set to OFF. This is a backward operation from the second operation operation position P2 to the first operation operation position P1 (see FIG. 15 (d), arrow X3) in which “75” is in the “off” state. In the second step, the pressing member 350 is rotated in the left rotation direction in plan view to release the action of the pressing arm piece 353 on the threshing switch 401, and the threshing switch 401 is turned off to turn off the threshing clutch 57 It is a left operation (see FIG. 15 (d), arrow X4) from the first work operation position P1 to the stop operation position P0. The third step is a backward operation from the stop operation position P0 to the reverse operation position P3 (see FIG. 15 (d), arrow X5) for turning on the cropping reverse rotation.

  Here, when performing the third step operation from the stop operation position P0 to the reverse operation position P3, as shown in FIG. 18, the movement of the working clutch lever 23 to the reverse operation position P3 is It is restricted. That is, since the forward upward movement of the first link 501 is restrained by the contact of the first contact portion 504 with the support shaft portion 323, centering on the first rotation axis S1 of the plate portion 311 In the right side view, the rotation in the left rotation direction (counterclockwise direction) is restricted, and the movement of the working clutch lever 23 to the reverse operation position P3 is suppressed. Therefore, in order to operate the working clutch lever 23 to the reverse operation position P3, it is necessary to release the check by the check unit 500.

  Therefore, in the state shown in FIG. 18, when the operator or the like depresses the parking brake pedal 601, as shown in FIG. 19, the forward upward movement of the first link 501 is not restrained. Thereby, the plate portion 311 is allowed to rotate in the left rotation direction (counterclockwise direction) around the first rotation axis S1 in a right side view, and the operator etc. can operate the working clutch lever 23 to the reverse operation position P3. It becomes. Thus, when the third step operation from the stop operation position P0 to the reverse operation position P3 is performed, the parking brake pedal 601 is depressed to the operation position Q2 (see FIG. 19), and then the stop operation position P0 is performed. To the reverse operation position P3.

  When the working clutch lever 23 is on the basis of the neutral state in which the stop operation position P0 is set, the reverse mechanism 110 is activated by the rearward operation of the working clutch lever 23 from the neutral state. Here, the threshing switch 401 is maintained in the OFF state. That is, since the position in the left-right direction of the working clutch lever 23 is constant between the stop operation position P0 and the reverse operation position P3, the rotation position of the pressing member 350 for turning off the threshing switch 401 is held. In this state, the rearward movement of the working clutch lever 23 is permitted by the recess 352 a of the engagement arm piece 352.

  As the work clutch lever 23 is moved from the stop operation position P0 to the reverse rotation operation position P3, as shown in FIG. 22 (a), the lever support pivot plate 310 is on the right side centering on the first pivot axis S1. The first arm 321 is pushed upward by the engagement pin 314 which penetrates the long hole 321a interlocking with this, and the pivoting arm 320 is moved to the third direction. It rotates rightward in the right side view about the rotation axis S3 (see arrow M5). As a result, the operation wire 145 pulled by the second arm 322 is loosened, and the pulling action of the claw member 130 by the operation wire 145 holding the claw member 130 in the non-engaging position is released. As a result, as shown in FIG. 23A, the biasing force of the spring 140 causes the claw member 130 to rotate in the engagement direction and engage with the gear 120 (see arrow M6), and the reaper input shaft 38 is a feeder house. 35 is engaged.

  Thus, the link mechanism 300 releases the tension of the operation wire 145 against the biasing force of the spring 140 against the claw member 130 by the stroke operation from the stop operation position P0 of the working clutch lever 23 to the reverse operation position P3. Is configured. Conversely, the link mechanism 300 resists the biasing force of the spring 140 by the stroke operation from the reverse operation position P3 of the working clutch lever 23 to the stop operation position P0, and disengages the claw member 130 from the engagement position It is configured to obtain a pulling action of the operation wire 145 moved and held in position.

  In the operating state of the reversing mechanism 110, that is, in the state where the reaper input shaft 38 is engaged with the feeder house 35, the reaper input shaft 38 is rotated in the reverse direction by the upward movement of the feeder 30, 36 will operate in the reverse direction. As a result, clogging of cereal grains in the feeder 30 is eliminated.

  Here, when clearing the clogging of the cereal grits in the feeder 30, the raising operation of the feeder 30 may be performed a plurality of times as needed by lowering the feeder 30 again. Then, when the feeder 30 descends in the operation state of the reversing mechanism 110, the relative rotation of the feeder house 35 with respect to the reaper input shaft 38 is permitted by the ratchet structure of the reverse mechanism 110, and in the forward direction of the reaper input shaft 38 Rotation is prevented or suppressed.

  After the clogging of cereal grits in the feeder 30 is eliminated, the combine clutch 1 is put in the work state by moving the work clutch lever 23 again to the first work operation position P1 and the second work operation position P2, and the work is resumed. Be done.

  When the reverse rotation mechanism 110 is in the operating state, the movement of the first link 501 to the rear upper side is restricted by the contact of the second contact portion 505 with the support shaft portion 323 as shown in FIG. There is. Thereby, the pivoting arm body 320 of the link mechanism 300 regulates the movement of the parking brake pedal 601 to the inoperative position Q1 by regulating the movement of the first link 501 of the check portion 500, and the parking brake mechanism Switching from the operating state to the non-operating state of 600 is disabled. Therefore, when the reversing mechanism 110 is in the operating state, the parking brake mechanism 600 can be switched from the operating state to the non-operating state unless the work clutch lever 23 is operated from the reverse operation position P3 to the stop operation position P0. Instead, the traveling machine body 2 is prevented from moving during the operation of clearing the clogging of the grain within the feeder 30.

  In the operation interlocking mechanism of the work clutch lever 23 and the reverse rotation mechanism 110 as described above, the claw member 130 of the reverse rotation mechanism 110 is engaged with the gear 120 by the link mechanism 300 according to the operation of the work clutch lever 23. From the mating position, it is operated to rotate in the opposite direction in two steps. That is, the claw member 130 is positioned at the disengagement position where the engagement with the gear 120 is released as a non-engagement position, and can be moved from this engagement release position to the retracted position rotated further in the opposite direction. It is configured. Specifically, it is as follows.

  Regarding the four operation positions of the work clutch lever 23, the reverse operation position P3 is the rear position, the stop operation position P0 and the first operation position P1 are the neutral position, and the second operation position P2 is the front position in the front and rear direction. It is divided into three positions.

  When the working clutch lever 23 is in the rear position (reverse operation position P3) as shown in FIG. 22 (a), the claw member 130 is engaged with the gear 120 as shown in FIG. 23 (a). Once in position, the reversing mechanism 110 is activated.

  When the work clutch lever 23 is operated from the rear position to the neutral position (stop operation position P0 or first work operation position P1), as shown in FIG. 22 (b), the lever support pivot plate 310 is viewed from the right side At the right rotation direction (see arrow M7), interlocking with this, the pivoting arm body 320 pivots in the left rotation direction in the right side view (see arrow M8), and the other end of the operation wire 145 Pulled forward (see arrow M9). As a result, as shown in FIG. 23B, the claw member 130 is pivoted in the opposite engagement direction against the biasing force of the spring 140 and reaches the disengagement position (see arrow M10). Becomes inoperative.

  Furthermore, as shown in FIG. 22 (c), the lever support rotating plate is operated by the operation clutch lever 23 being operated from the first operation operation position P1 which is the neutral position to the front position (second operation operation position P2). 310 is further rotated in the right rotation direction in the right side view (refer to arrow M2), interlocking with this, the first arm 321 is pushed downward by the engagement pin 314 penetrating the long hole 321a, and the rotation arm The body 320 further pivots in the left rotation direction in a right side view (see arrow M11). As a result, the other end of the operation wire 145 connected to the second arm 322 is further pulled forward (see arrow M12). As a result, as shown in FIG. 23C, the claw member 130 is further pivoted in the opposite engagement direction against the biasing force of the spring 140 and reaches the retracted position (see the arrow M13). That is, the claw member 130 in the engagement release position is further rotated in the opposite engagement direction from the engagement release position as the reaper clutch 75 is turned "on" by the operation of the work clutch lever 23. Rotate to the retracted position.

  As described above, the link mechanism 300 for interlockingly connecting the claw member 130 of the reverse rotation mechanism 110 and the working clutch lever 23 with each other interlocks by moving the working clutch lever 23 from the reverse rotation operation position P3 to the stop operation position P0. The claw member 130 is engaged by moving the work clutch lever 23 from the first work operation position P1 to the second work operation position P2 by moving 130 to the engagement release position where the engagement with the gear 120 is released. It is configured to move from the release position to the retracted position further moved in the engagement release direction (anti-engagement direction).

  Further, in the combine 1 of the present embodiment provided with the reverse rotation mechanism 110, the controller 400 for controlling the start of the engine 25 controls the start and stop of the engine 25 based on the detection signal from the reverse switch 403.

  As described above, the reverse rotation switch 403 detects that the working clutch lever 23 is in the reverse rotation operation position P3. Therefore, in a state where the detection signal from the reverse rotation switch 403 is input to the controller 400, the controller 400 controls so as not to start the engine 25. That is, the controller 400 performs control to disable the start of the engine 25 in a state in which the reverse rotation switch 403 detects that the working clutch lever 23 is positioned at the reverse rotation operation position P3. An example of a configuration for performing such control will be described.

  As shown in FIG. 21, the controller 400 is connected to the battery 406 via a starter switch 405 for applying power. The starter switch 405 is a rotary switch or a push button switch which can be rotationally operated by inserting a predetermined key into a key hole, and is provided, for example, in a steering column located in front of the driver's seat 17 in the driving unit 15.

  Normally, when the starter switch 405 is turned ON, the current from the battery 406 flows into the coil portion of the starter relay connected to the starter, and the switch portion of the starter relay becomes conductive. As a result, the starter operates by energization from the battery 406, and the engine 25 is started. After the engine 25 is started, the driving state of the engine 25 and the power supply from the battery 406 to each part are maintained. When the starter switch 405 is turned OFF, the power supply from the battery 406 is stopped and the driving of the engine 25 is stopped.

  In such a configuration, when the controller 400 detects that the working clutch lever 23 is in the reverse operation position P3 based on the detection signal from the reverse switch 403, the starter switch 405 is turned on when the engine 25 is started. The engine 25 is not started even by being operated. That is, the controller 400 performs control such that the current from the battery 406 does not flow into the coil portion of the starter relay so that the cut-off state (non-conduction state) of the switch portion of the starter relay is maintained Do. As a result, the energization from the battery 406 to the starter is cut off and the starter does not operate, and as a result, the engine 25 does not start.

  In the start / stop control of the engine 25 based on the detection signal of the reverse switch 403, for example, an alarm buzzer sounds or in a display unit such as a liquid crystal display provided in the operation unit 15, for example, Turn off and start the engine. The warning message such as "" may be displayed. Thus, the operator's attention can be drawn, and the fact that the engine 25 can not be started can be accurately notified.

  Further, the controller 400 controls the engine 25 not to start in a state where a detection signal from the engine start permission switch 700 is not input to the controller 400. That is, in the state where the parking brake pedal 601 is in the inoperative position Q1 (see FIG. 18), the controller 400 causes the parking brake pedal 601 to operate at the operating position Q2 (FIG. The engine 25 is permitted to be started by detecting the state of 19). Incidentally, also for the start / stop control of the engine 25 based on the detection signal of the engine start permission switch 700, a configuration similar to the start / stop control of the engine 25 based on the detection signal of the reverse switch 403 can be adopted. I omit it.

  Also, in the start / stop control of the engine 25 based on the detection signal of the engine start permission switch 700, for example, an alarm buzzer sounds or a display unit such as a liquid crystal display device provided in the operation unit 15 Start the engine with the "working position". The warning message such as "" may be displayed. Thus, the operator's attention can be drawn, and the fact that the engine 25 can not be started can be accurately notified.

  According to the combine 1 of the present embodiment having the above configuration, the structure is complicated in the configuration provided with the feeder 30 for transporting / supplying the grain scale cut by the harvesting unit 3 to the threshing unit 7 By the simple structure, it is possible to allow the operation of the conveyor 36 in the reverse direction of the feeder 30 and eliminate the clogging of the grain scale in the feeder 30 without causing the

  That is, the combine 1 according to the present embodiment causes the conveyor 36 to be forced in the reverse direction by using the raising operation of the feeder 30 by bringing the reaper input shaft 38 into engagement with the feeder house 35 by the reversing mechanism 110. It has a configuration to rotate it. That is, the conveyor 36 is rotated in the reverse direction by the power unrelated to the transmission system for driving the working units such as the reaper 3 and the threshing unit 7.

  Thus, in comparison with the conventional configuration in which the transmission mechanism for reverse rotation of the conveyor is provided in the power transmission path from the engine to the reaper, the conveyor does not particularly change the motive power transmission configuration from the engine 25 to the reaper 3 It is possible to realize the configuration for operating the 36 in the reverse direction with an inexpensive and simple configuration. Further, since the reverse rotation mechanism 110 according to the present embodiment operates the conveyor 36 in the reverse direction by using the lifting operation of the feeder 30 by the lifting and lowering cylinders 39, hydraulic pressure for operating the lifting and lowering cylinders 39 and the like in the combine 1 There is no need to change the apparatus in particular, nor is it necessary to use extra power to operate the conveyor 36 in the reverse direction.

  Further, since the feeder 30 ascends by the action of hydraulic pressure by the elevating cylinder 39, the ascent operation of the feeder 30 can easily obtain a large operating force as compared to the ascent operation of the feeder 30 by its own weight. For this reason, even in a state where the feeder 30 does not easily go up and down due to, for example, the clogging effect of the grain gutter in the feeder house 35, the feeder 30 can be reliably raised, and the reverse operation of the conveyor 36 by the reverse mechanism 110 is reliably obtained. It becomes possible. Further, since the raising operation of the feeder 30 is actively performed by the operation of the elevating cylinder 39, the operation control is easier to perform than the lowering operation of the feeder 30 by its own weight. Good operability can be obtained for the reverse operation.

  Moreover, according to the reversing mechanism 110 according to the present embodiment, the reversing mechanism 110 can be configured regardless of the power transmission path from the engine 25 to the reaper 3. For this reason, there is no need to provide a structure for avoiding interference between the power transmissions for forward and reverse rotation of the conveyor 36 in the power transmission path from the engine 25 to the reaper 3, resulting in a complicated structure and a device configuration. It is possible to configure the conveyor 36 to operate in the reverse direction without becoming large.

  Further, the reversing mechanism 110 according to the present embodiment is mainly configured by the gear 120 supported by the reaper input shaft 38 and the claw member 130 supported by the feeder house 35 and provided on the feeder 30 side. There is. According to such a configuration, the reversing mechanism 110 can be realized with a very simple configuration, and can be easily provided to the existing configuration of the combine 1.

  In addition, the reversing mechanism 110 according to the present embodiment raises and lowers the feeder 30 by rotating the cutting input shaft 38 in the reverse direction in the operating state of the reversing mechanism 110 by the gear 120 and the claw member 130. It is configured as a ratchet mechanism that limits to. According to such a configuration, the feeder 30 can be rotated relative to the reaper input shaft 38 when the feeder 30 is lowered in the operation state of the reverse rotation mechanism 110. For this reason, when removing clogging of the grain gravel in the feeder 30, by raising and lowering the feeder 30, the conveyor 30 is operated in the reverse direction by the raising operation of the feeder 30 a plurality of times. Can be done smoothly.

  Moreover, the combine 1 according to the present embodiment receives the transmission of the raising operation of the feeder 30 via the claw member 130, amplifies the amount of rotation of the gear 120 which rotates, and transmits the amplification mechanism 200 for transmitting to the reaper input shaft 38. Prepare. According to such a configuration, it is possible to obtain a sufficient amount of rotation for the reverse rotation of the reaper input shaft 38 for operating the conveyor 36 in the reverse direction while utilizing the elevating operation of the feeder 30. That is, since the operation stroke of the raising and lowering operation of the feeder 30 is limited, a sufficient amount of rotation may not be obtained in order to eliminate the clogging of the gravel about the rotation of the reaper input shaft 38 in the reverse direction. However, by providing the amplification mechanism 200, it is possible to amplify the amount of rotation of the reaper input shaft 38 due to the rotation of the gear 120 along with the upward rotation of the feeder 30. As a result, a sufficient amount of movement can be easily obtained for the reverse movement of the conveyor 36, and clogging of grain can be effectively eliminated.

  Further, the amplification mechanism 200 is supported by the input shaft side gear (first gear 211 and fourth gear 214) supported by the reaper input shaft 38, the idler shaft 215, and the idler shaft 215, and meshes with the input shaft side gear. The transmission shaft side gear (second gear 212 and third gear 213) is included. According to such a configuration, the amplification mechanism 200 can be simply configured by utilizing the existing configuration, and the amplification effect of the rotation amount by the amplification mechanism 200 can be reliably and easily obtained.

  Further, the reversing mechanism 110 according to the present embodiment is provided on the left side of the feeder 30, which is the left and right outside of the machine with respect to the feeder house 35 in the feeder 30. According to such a configuration, since the arrangement portion of the reversing mechanism 110 is the outer left portion of the combine 1, the accessibility to the reversing mechanism 110 can be improved. Thereby, good maintainability can be obtained for the reversing mechanism 110. Therefore, for example, assuming that the arrangement of the feeders 30 of the cabin 16 is reverse to the combine 1 according to the present embodiment, the reversing mechanism 110 is the right side that is the left and right outer side of the machine with respect to the feeder house 35 Is preferably provided.

  Further, the combine 1 according to the present embodiment is configured to operate the operation of the reverse rotation mechanism 110 by the work clutch lever 23 provided in the drive unit 15. According to such a configuration, the operator in driving operation in the driving unit 15 can operate the reversing mechanism 110 without leaving the driver's seat 17, so that it is good in removing clogging of grain Operability can be obtained.

  That is, for example, according to the configuration in which the operating tool for operating the reversing mechanism 110 is separately provided, the operation target by the operator increases and the operation becomes complicated, and the operating tool for operating the reversing mechanism 110 is, for example, a cabin. According to the configuration disposed outside the operation unit 15 such as the position between the feeder 16 and the feeder 30, it is difficult for the operator to operate the operation tool for operating the reversing mechanism 110 while sitting on the driver's seat 17 In some cases, good operability can not be obtained. Then, the operability of the reverse operation of the conveyor 36 can be improved by using the working clutch lever 23 provided in the operation unit 15 as the operating tool of the reverse mechanism 110 as in the combine 1 of the present embodiment.

  In addition, by adopting a configuration in which the reverse rotation mechanism 110 is operated by the working clutch lever 23, the existing operating tool provided in the operation unit 15 can be shared as the operating tool for the reverse rotation mechanism 110. It is necessary to separately provide an operation unit for operation, and the configuration of various operation units disposed in the operation unit 15 can be simplified.

  Furthermore, for example, in the case where the reversing mechanism 110 is operated by an operation tool provided separately from the working clutch lever 23, the reaper clutch 75 and the reversing mechanism 110 are operated independently of each other, so the reaper clutch A configuration is required to prevent the reverse rotation mechanism 110 from operating (forward and reverse biting) with 75 in the ON state. In this respect, by adopting a configuration in which the reverse rotation mechanism 110 is operated by the working clutch lever 23, common use of the operating tools of the reaper clutch 75 and the reverse rotation mechanism 110 can be achieved. By making the operation of the reversing mechanism 110 different from each other, it is possible to reliably avoid both normal and reverse bites.

  Further, in the present embodiment, the claw member 130 is connected to the working clutch lever 23 by the link mechanism 300 including the operation wire 145, and is biased in the direction of engaging with the gear 120 by the spring 140. A configuration is employed in which the engagement of the claw member 130 with the gear 120 is maintained by pulling the spring 130 against the spring 140 with the operation wire 145. According to such a configuration, when disengaging the claw member 130 and bringing the reverse rotation mechanism 110 into the inoperative state, the claw member 130 is reliably pulled by the operation wire 145, whereby the engagement of the claw member 130 is ensured. Can be released.

  That is, if a configuration is adopted in which the engagement of the claw member 130 is released by the biasing force of the spring, the operation of the working clutch lever 23 is not sufficiently transmitted to the claw member 130 via the spring depending on the state of the spring. In addition, there may be a problem that the claw member 130 remains in the state of being engaged with the gear 120 by the action of the spring. Therefore, by adopting the tension operation wire 145 as the operation member for releasing the engagement of the claw member 130, the operation of the work clutch lever 23 can be reliably transmitted to the claw member 130. Biting can be prevented, and the operation of the working clutch lever 23 enables the reverse mechanism 110 to be reliably inactivated. Further, by using the biasing force of the spring 140 for the rotation of the claw member 130 in the engagement direction, the claw member 130 is compared with, for example, a configuration using a wire separately from the operation wire 145 for engagement release. It is possible to realize the structure for operating the device with a simple configuration.

  Further, in the present embodiment, the link mechanism 300 which connects the claw member 130 and the working clutch lever 23 to each other is engaged with the claw member 130 from the engagement position in accordance with the operation position of the work clutch lever 23 in the front-rear direction. It is configured to rotate in two steps of the engagement release position and the retraction position in the coupling direction. According to such a configuration, the claw member 130 is engaged with the operation clutch lever 23 at the operation position where the operation of the reaper 3 which will directly interfere with the operation of the reversing mechanism 110 is turned ON. It is possible to be evacuated from the Thus, engagement of the claw member 130 with the gear 120 can be reliably prevented while the reaper 3 is in operation, and high safety can be obtained.

  Moreover, the combine 1 of this embodiment is provided with the reverse rotation switch 403, and the controller 400 performs start / stop control of the engine 25 based on the detection signal. According to such a configuration, it is possible to prevent the engine 25 from being started in a state where the working clutch lever 23 is in the reverse operation position P3 in which the reverse mechanism 110 is in operation (removing reverse ON state). Thus, for example, by raising the feeder 30 after starting of the engine 25 in the state of the reaper reverse rotation ON state, the reaper input shaft 38 is rotated in the reverse direction, and the reaper input shaft 38 is rotated, thereby the reaper input shaft It is possible to solve the problem that the respective operating units of the reaper 3 such as the conveyor 36 and the reaper unit 32 which operates by receiving the transmission of power from the vehicle 38 operate unintentionally. As a result, high security can be obtained.

[Another embodiment]
Another embodiment of the present invention will be described. In addition, the configuration of each embodiment described below is not limited to being individually applied, and may be applied in combination with the configuration of the other embodiments.

(1) In the above embodiment, although the check control unit 500 can switch between the check control state and the check control release state in conjunction with the parking brake mechanism 600 being switched between the operating state and the non-operating state, the check portion However, regardless of the parking brake mechanism 600, it is possible to switch between the check state and the check release state, and it is possible to appropriately change how the check portion is configured.

  For example, the check control unit checks the movement of various components in the link mechanism 300, such as checking the movement of the pivoting arm body 320, or directly restricts the movement of the working clutch lever 23, thereby suppressing the check. It can also be configured to be switchable to the state. As described above, when the components of the link mechanism 300 and the operation clutch lever 23 are restrained, for example, when the operation clutch lever 23 is operated to the reverse operation position P3, the components and operations of the link mechanism 300 The movement of the clutch lever 23 is restrained to maintain the tension applied to the operation wire 145 in the link mechanism 300. Then, when a predetermined time elapses from the time when the work clutch lever 23 is operated to the reverse rotation operation position P3, it is determined that the predetermined condition is satisfied, and mechanical force of the link mechanism 300 is utilized using the biasing force of the biasing body. By restricting the movement of the component members and the working clutch lever 23, the application of the pulling action to the operation wire 145 can be released, and the state can be switched to the check release state. The predetermined time may be, for example, the time required for the rotation of the reaper input shaft 38 to stop and the rotation of the conveyor 36 in the forward direction to stop.

  Further, in place of the link mechanism 300 etc., a reverse rotation mechanism actuator capable of switching the reverse rotation mechanism 110 between the operating state and the non-operating state is provided, and the working clutch lever 23 is moved to the reverse rotation operating position P3 by the reverse rotation switch 403 At the time of detecting that, when the predetermined time elapses from the time when the check portion maintains the check condition and the reverse switch 403 detects that the working clutch lever 23 is moved to the reverse operation position P3, the check portion checks The reverse rotation mechanism 110 can be switched to the operating state by activating the reverse rotation mechanism actuator in the released state. As described above, in the above-described embodiment, the mechanical configuration is used as the check control unit to check against the movement of the work clutch lever 23 etc. However, the electrical arrangement using the reverse switch 403, the reverse mechanism actuator, etc. Can also be adopted.

  Furthermore, in the above embodiment, the operation movement path connecting the second operation position P2 and the first operation position P1 is orthogonal to the operation movement path connecting the first operation position P1 and the stop operation position P0. The operation movement path connecting the operation position P1 and the stop operation position P0 and the operation movement path connecting the stop operation position P0 and the reverse operation position P3 are orthogonal to each other. The movement of the working clutch lever 23 to the reverse operation position P3 can also be restrained by changing the shape of the operation movement path leading to the operation position P3.

  For example, with regard to the operation movement path connecting the first operation operation position P1 and the stop operation position P0, the operation clutch lever 23 is temporarily moved in the forward direction and then moved in the backward direction to be moved. The movement of the clutch lever 23 to the reverse operation position P3 can be restrained. In this case, it takes a predetermined time to operate the working clutch lever 23 to the reverse rotation operation position P3, and the predetermined time is satisfied because the time required to operate the working clutch lever 23 is a predetermined time. It will be.

  In addition, between the stop operation position P0 and the reverse operation position P3, by providing a manual operation type restricting portion for checking the movement of the work clutch lever 23 to the reverse operation position P3 by abutting on the work clutch lever 23. You can also. In this case, the operator or the like operates the restricting portion while the work clutch lever 23 is positioned at the stop operation position P0, thereby moving the restricting portion to the retracted position not in contact with the work clutch lever 23, The movement of the work clutch lever 23 to the reverse operation position P3 is permitted. Furthermore, when the work clutch lever 23 is moved from the stop operation position P0 to the reverse operation position P3, the reverse operation position P3 of the work clutch lever 23 is also applied by giving a larger resistance than when moved to another operation position. It is possible to check the movement to Even in such a case, it takes a predetermined time to operate the working clutch lever 23 to the reverse rotation operating position P3, and the predetermined time is satisfied because the time required to operate the working clutch lever 23 is a predetermined time. It will be done.

(2) In the above embodiment, the lifting and lowering cylinder 39 for lifting and lowering the feeder 30 is a single-acting hydraulic cylinder for applying hydraulic pressure when lifting the feeder 30, but the invention is not limited thereto. 39 may be a reciprocating cylinder.

(3) In the above embodiment, the working clutch lever 23 for operating the reaper 3 and the threshing part 7 is used as an operating tool for operating the reversing mechanism 110, but the invention is not limited to this. Absent. The operating tool for operating the reversing mechanism 110 is an operating tool for performing either one of the reaping unit 3 and the threshing unit 7, or an operating tool provided separately for operating the reversing mechanism 110. You may However, from the viewpoint of simplifying the configuration by utilizing the existing configuration or avoiding the simultaneous operating state of the working unit such as the reaper 3 and the like and the reversing mechanism 110, the operating tool of the reversing mechanism 110 It is preferable that it is a work operation tool for performing the operation of at least one of the reaper 3 and the threshing part 7.

(4) In the above embodiment, the lever guide portion 150 of the working clutch lever 23 has a generally crank shape as a whole by the first movement path portion 161, the second movement path portion 162, and the third movement path portion 163. Although it is configured to do, it is not limited to this. In the lever guide portion 150, the direction (second direction) along which the third movement path portion 163 from the stop operation position P0 to the reverse rotation operation position P3 is the first direction from the stop operation position P0 to the first work operation position P1. The movement path portion 161 may be in a direction different from the direction (first direction) along which the movement path portion 161 follows. Therefore, for example, the third movement path portion 163 is provided forward from the stop operation position P0, and the lever guide portion 150 has a substantially "U" shape as a whole by each movement path portion. It is also good.

(5) In the above embodiment, as the start / stop control of the engine 25, the controller 400 performs control to stop the start of the engine 25 by shutting off the energization from the battery 406 to the starter. It is not a thing.

1 Combine 2 Running aircraft (airframe)
3 reaper 7 threshing portion 23 work clutch lever (work operation tool)
36 Conveyor (Transporter)
38 reaper input shaft (transport mechanism)
110 Reverse mechanism (rotation control part)
300 link mechanism (interlocking mechanism for rotation restriction part)
500 check control unit 600 parking brake mechanism (aircraft movement control unit)
601 Parking brake pedal (machine movement regulation operating tool)

Claims (6)

A reaper that reaps grain weirs,
And a transport unit that transports the grain remnants harvested by the reaper to the threshing unit,
The transport unit transports the grain scraps cut by rotation in one direction to the threshing part, and restricts rotation in one direction by the transport mechanism to turn the transport mechanism into a restricted state. The control unit includes: a control unit; and a check control unit that controls the transfer mechanism from being in a control state until a predetermined condition is established.
The combine mechanism is configured such that the transport mechanism is configured to be rotatable in a direction opposite to the one direction in a restricted state by the rotation restricting portion. An airframe having the reaper portion, the transport portion, and the threshing portion;
And a movement control unit for restricting the movement of the machine body by being activated.
The combine according to claim 1, wherein the predetermined condition includes that the machine body movement restriction unit is in an operating state.   The combine according to claim 2, wherein the machine body movement restricting portion is configured to be incapable of switching from the operating state to the inoperative state in a state where the transport mechanism is in the restricting state by the rotation restricting portion. A work operation tool for operating the reaper and the transport unit;
As an operation position of the work operation tool, the operation operation position for operating the reaper in an operating state and rotating the transport mechanism in the one direction, and setting the reaper in a non-operating state to the one direction in the transport mechanism Reverse operation for stopping the rotational drive of the motor and for stopping the transport mechanism in the opposite direction to the one direction by setting the transport mechanism in the control state by setting the cutting mechanism in the non-operating state and the rotation control portion Including position and
The control device is configured to be able to check that the transport mechanism is in the restricted state by holding the movement of the work operation tool to the reverse operation position until the predetermined condition is satisfied. The combine according to any one of 3. An airframe having the reaper portion, the transport portion, and the threshing portion;
An airframe movement restricting portion which restricts the movement of the airframe by being activated;
An aircraft movement regulation operating tool for operating the aircraft movement regulation unit;
The operation position of the machine movement restricting operation tool includes a non-operating position where the machine movement restricting portion is inactivated, and an operation position where the machine movement restricting portion is activated.
The check control unit is movable in conjunction with the movement of the machine movement restricting operation tool, and when the machine movement restricting operation tool is positioned at the inoperative position, the transport mechanism is in the restriction state. A switch to a check control state in which check control is performed, and in response to the movement of the machine movement regulation operating tool to the operation position, the switch control release state in which the check control state is released is switched to the check release state. The combine according to any one of the above. The rotation restricting portion interlocking mechanism operates the rotation restricting portion in conjunction with the movement of the work operation tool to the reverse rotation operation position, and the rotation restricting portion sets the transport mechanism in a restricting state.
The check control unit is configured to be able to check that the transport mechanism is in a restriction state by checking the movement of the rotation restriction unit interlocking mechanism until the predetermined condition is satisfied.
The rotation control unit interlocking mechanism restricts the movement of the check control unit in a state where the work operation tool is positioned at the reverse rotation operation position and the transport mechanism is in the control state, thereby the machine movement control unit The combine according to claim 5, wherein switching from the operating state to the non-operating state is disabled.