JP2020022509A - Combine - Google Patents

Abstract

To provide a combine with a conveying device for conveying and supplying reaped grain culm to a threshing unit in which a motion to a reverse direction of a conveyor in the conveying device is enabled by a simple structure without causing complication of a structure, and thereby the clogging of the grain culm in the conveying device can be eliminated.SOLUTION: A combine includes a feeder 30 for conveying grain culm reaped by a reaping unit and supplying it to a threshing unit 7. The feeder 30 has a conveyor 36 using a reaper input shaft 38 for receiving transmission of power as a drive shaft by using right and left directions as an axial direction, in a feeder house 35, and is provided so as to be lifted and lowered by the turning mainly on the reaper input shaft 38 to a body of the combine. The feeder includes a reversing mechanism 110 for transmitting a lifting motion of the feeder 30 to the reaper input shaft 38, and turning the reaper input shaft 38 in a reverse direction to the rotating direction in the conveyance of the grain culm with the lifting motion of the feeder 30. The reversing mechanism 110 is provided in the outside of right and left directions of a rear end of the feeder 30.SELECTED DRAWING: Figure 8

Description

  TECHNICAL FIELD The present invention relates to a combine provided with a transport device that transports grain stalks cut by a cutting unit and supplies the culms to a threshing unit.

  2. Description of the Related Art Conventionally, there has been a combine provided with a feeder, which is a transport device that transports grain culms cut by a cutting unit and supplies the culms to a threshing unit. The feeder has a configuration in which a conveyor for transporting grain culm is provided in a feeder house as a housing. The conveyor has a cutting input shaft whose axial direction is the left-right direction as a drive shaft of the conveyor that supports the feed end side.

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

  Some combiners having such a configuration have a configuration for reversing the conveyor in order to solve the clogging of the cereal stalk in preparation for the case where the cereal stalk is clogged with the feeder (for example, Patent Document 1, 2).

  Patent Document 1 discloses a configuration in which a power transmission mechanism including a reverse gear, a slide gear, and the like is incorporated in a counter case provided on a side of the engine in a power transmission mechanism between an output shaft of the engine and a reaping unit. It has been disclosed. A forward / reverse rotation of the cutting output shaft for extracting power from the counter case is switched by a power switching mechanism in the counter case.

  Patent Document 2 discloses a reversing mechanism for reversing the rotation transmitted to a cutting input shaft serving as a conveyor input shaft of a feeder, a handling cylinder input shaft for rotating a handling cylinder of a threshing unit by receiving power of an engine, and a cutting input. A configuration provided in a transmission mechanism between the shaft and the shaft is disclosed. The reversing mechanism of Patent Document 2 includes a pulley, a belt, and a gear for transmitting power for reversing the cutting input shaft, and a shaft for supporting these.

JP 2004-121123 A JP-A-2006-136924

  All of the above-described conventional technologies have a configuration in which a reverse rotation transmission mechanism for reversely rotating a conveyor is provided in a path for transmitting power from an engine to a cutting unit. For this reason, the power transmission mechanism from the engine to the reaping unit becomes structurally complicated, the number of parts increases, and the cost is disadvantageous. Further, according to the configuration in which the power transmission mechanism for reverse rotation is provided in a manner branched from the power transmission path for normal rotation of the cutting input shaft as in the configuration of Patent Document 2, the power transmission mechanism for forward / reverse rotation is provided. A structure is required to avoid mutual interference. For this reason, there are problems that the structure becomes complicated and the device configuration becomes large.

  The present invention has been made in view of the above-described problems, and in a configuration including a transport device that transports / supplies cereal stalks mowed by the mowing unit to the threshing unit, the structure is complicated. An object of the present invention is to provide a combine that enables a conveyor to operate in a reverse direction with a simple structure without inviting, and that can eliminate clogging of grain stalks in the transfer device.

  The combine according to the present invention is a combine provided with a transport device that transports the grain stalks mowed by the mowing unit and supplies the grain culm to the threshing unit, wherein the transport device has an axial direction in a left-right direction in a housing. A conveyor having an input shaft that receives power transmission as a drive shaft, and is provided so as to ascend and descend by turning about the input shaft with respect to the combine machine. A reversing mechanism is provided for transmitting the ascending operation to the input shaft and rotating the input shaft in a direction opposite to the rotation direction during the transportation of the cereal stem with the ascending operation of the transport device.

  Further, in a combine according to another aspect of the present invention, in the combine, the reverse rotation mechanism is supported by a first engagement member supported by a protruding portion of the input shaft from inside the housing, and supported by the transfer device. A second engaging member that transmits the ascending operation of the transport device to the input shaft via the first engaging member by engaging with the first engaging member. Have

  In the combine according to another aspect of the present invention, in the combine, the reverse rotation mechanism may be configured such that the first engagement member is a gear supported by the input shaft, and the second engagement member is A pawl member urged in a direction to be engaged with the gear includes a ratchet mechanism for restricting a lifting operation of the transfer device for rotating the input shaft via the gear to a lifting operation of the transfer device.

  Further, in the combine according to another aspect of the present invention, in the combine, the amount of rotation of the first engagement member that rotates by receiving the transmission of the ascent operation of the transport device via the second engagement member may be reduced. An amplification mechanism for amplifying and transmitting the amplified signal to the input shaft is provided.

  Further, in a combine according to another aspect of the present invention, in the combine, the reversing mechanism is provided on a laterally outer side of the main unit, among laterals of the housing. .

  Further, in the combine according to another aspect of the present invention, in the combine, the operation / non-operation of the reverse rotation mechanism is performed by operating a work operation tool for performing at least one operation of the cutting unit and the threshing unit. It is configured to be operated.

  ADVANTAGE OF THE INVENTION According to this invention, in the structure provided with the conveyance apparatus which conveys and feeds the cereal stalks cut by the cutting part to the threshing part, the conveyer in a conveyance apparatus is simple and without a complicated structure. Can be operated in the reverse direction, and clogging of the grain stalk in the transport device can be eliminated.

It is a left view of the combine concerning one embodiment of the present invention. It is a right view of the combine concerning one embodiment of the present invention. It is a top view of a 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 view which shows the structure of the feeder which concerns on one Embodiment of this invention, and its vicinity. It is a left view which shows the structure of the feeder which concerns on one Embodiment of this invention. It is a top view showing the rear part of a feeder concerning one embodiment of the present invention. It is a perspective view showing the rear part of a feeder concerning one embodiment of the present invention. It is a perspective view showing the composition of the reversing mechanism concerning one embodiment of the present invention. It is a left side view showing the reversing mechanism concerning one embodiment of the present invention. FIG. 2 is a plan view showing a reverse rotation mechanism and an amplification mechanism according to one embodiment of the present invention. FIG. 3 is a rear cross-sectional view illustrating a reverse rotation mechanism and an amplification mechanism according to an embodiment of the present invention. FIG. 2 is a schematic diagram illustrating a reverse rotation mechanism and an amplification mechanism according to an embodiment of the present invention. It is a figure showing composition of a work clutch lever concerning one embodiment of the present invention. FIG. 4 is an explanatory diagram illustrating an operation mode of a work clutch lever according to an embodiment of the present invention. It is a perspective view showing a work clutch lever and a link mechanism concerning one embodiment of the present invention. FIG. 3 is a plan view showing a work clutch lever and a link mechanism according to one embodiment of the present invention. It is a control block diagram concerning one embodiment of the present invention. It is operation | movement explanatory drawing of the working clutch lever and link mechanism which concern on one Embodiment of this invention. It is operation | movement explanatory drawing of the reverse rotation mechanism which concerns on one Embodiment of this invention.

  The present invention relates to a configuration in which a conveying device that conveys a grain stalk cut by a cutting unit and supplies the culm to a threshing unit is provided so as to be rotatable up and down about a cutting input shaft as a rotation axis. The present invention is intended to eliminate the clogging of grain stalks in the transport device by using a simple structure by enabling the conveyor of the transport device to operate in the reverse direction using. Hereinafter, embodiments of the present invention will be described.

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

  As shown in FIGS. 1 and 2, a combine 1 according to the present embodiment is a harvester that can scrape a harvested field crop into a machine body, thresh, sort, store grains, and appropriately carry out the machine outside the machine. It is a normal type combine. The combine 1 has a traveling body 2 capable of self-propelling, and a reaper 3 provided at a front end of the traveling body 2. The reaping unit 3 is configured as a reaping device that captures uncut culms such as rice and wheat while cutting the culm, and is attached to the traveling machine body 2 so as to be able to move up and down.

  The traveling machine body 2 includes a traveling section 4 configured as a crawler traveling apparatus having a pair of left and right crawler sections 5 and 5. A body frame 6 is provided between the left and right crawlers 5 and 5. Each crawler section 5 includes a plurality of rotating bodies including a driving sprocket 5a provided at a front end thereof and a tension roller 5b provided at a rear end of the crawler section 5, and a crawler belt 5c wound around these rotating bodies. And The plurality of rotating bodies constituting the crawler unit 5 are provided on a track frame 5d provided on the lower surface side of the traveling body 2. Further, the driving sprocket 5 a is driven to rotate by receiving the power of the engine 25 provided in the combine 1.

  On the left side of the machine frame 6, a threshing unit 7 for threshing the grain stalks cut and supplied by the cutting unit 3 and a sorting unit 8 for sorting the grains threshed by the threshing unit 7 are provided. . The threshing unit 7 and the sorting unit 8 are arranged in such a manner that the threshing unit 7 is in the upper stage and the sorting unit 8 is in the lower stage.

  On the machine body frame 6, a grain storage unit 9 having a Glen tank 10 for storing the grains (clean grains) sorted by the sorting unit 8 is provided to the right of the threshing unit 7 and the sorting unit 8. . A lower discharge conveyor 11 that conveys the stored grains toward the discharge port of the Glen tank 10 is provided in the Glen tank 10 (see FIG. 4). A vertical transport conveyor 12 is provided upright along the vertical direction so as to communicate with the discharge port of the Glen tank 10. A grain discharge conveyor 13 is connected to the upper end of the vertical conveyor 12. The grain discharge conveyor 13 is provided so as to be capable of turning horizontally and swinging up and down around a horizontal axis. The grains in the Glen tank 10 are conveyed by these conveyors, and are discharged to a truck bed, a container, or the like from a paddy port 14 provided at the tip of the grain discharge conveyor 13.

  Further, on the body frame 6, at a position in front of the grain storage unit 9, that is, at a position on the right front part on the body frame 6, an operation unit 15 on which an operator is mounted is provided. The operation unit 15 is covered by a cabin 16. The driving section 15 is provided with a driving seat 17, a steering handle 18 disposed in front of the driving seat 17, a main transmission lever 21, an auxiliary transmission lever 22, a work clutch lever 23, and the like. The work clutch lever 23 is a work operation tool for turning on and off the threshing clutch 57 and the reaping clutch 75 (see FIG. 4). The main transmission lever 21, the auxiliary transmission lever 22, and the work clutch lever 23 are arranged on a lever column 24 provided on the left side of the driver's seat 17.

  An engine 25 as a drive source is provided behind the grain storage unit 9 on the traveling body 2. The engine 25 is a diesel engine and has a diesel particulate filter (DPF) 26 as an exhaust gas purifying device. The DPF 26 collects particulate matter mainly composed of black smoke in the exhaust gas discharged from the engine 25. The engine 25 purifies the exhaust gas by passing the exhaust gas through the DPF 26.

  The reaper 3 will be described. The cutting unit 3 includes a feeder 30 as a transport device, a grain header (platform) 31, a cutting blade device 32, a pair of right and left weeds 33, 33, and a scraping reel.

  The feeder 30 is a conveying device that conveys the grain stalks cut by the cutting unit 3 and supplies the culms to the threshing unit 7. The feeder 30 includes a feeder house 35 as a housing, and a conveyor 36 provided in the feeder house 35 for transporting grain stalks. The feeder 30 is located on the left side of the cabin 16, and has a rear end opening of a feeder house 35 which is formed in a substantially rectangular cylindrical shape whose longitudinal direction is the front-rear direction in plan view, and is provided in the front opening 7 a of the threshing unit 7. It is provided in a state where it is communicated.

  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 mounted on a shaft with the left-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 clipper. The pair of left and right weeds 33, 33 is provided so as to protrude forward from the left and right sides on the front side of the grain header 31. The scraping reel 34 is a reel with a tine bar, and is provided at a position above and in front of the scraping auger 37. The scraping reel 34 is rotatably supported between the distal ends of a pair of left and right reel support arms 34a, 34a whose base ends are pivotally supported by the grain header 31, with the left-right direction being the rotation axis direction. The scraping reel 34 continuously acts on the pod portion of the grain stalk while rotating, and scrapes the pod portion of the grain stalk toward the scraping auger 37 side. The power of the engine 25 transmitted through various transmission mechanisms is used for the operation of each part of the mowing unit 3.

  The conveyor 36 in the feeder house 35 has a cutting input shaft (feeder house conveyor shaft) 38 provided at the front of the threshing unit 7 and having a left-right direction as an axial direction, as a drive shaft for supporting the feed end side thereof. The rear end of the feeder 30 is rotatably supported by the cutting input shaft 38 with the left-right direction as the rotation axis direction. An elevating cylinder 39 is interposed between the lower surface of the feeder house 35 and the body frame 6.

  The elevating cylinder 39 is a single-acting hydraulic cylinder that exerts a hydraulic action when extended. Therefore, the mowing unit 3 (feeder 30) rotates in the ascending direction by extending the lifting / lowering cylinder 39 with the action of hydraulic pressure, and the hydraulic pressure of the lifting / lowering cylinder 39 is released. As the feeder 30) descends due to its own weight, the lifting cylinder 39 is shortened.

  With such a configuration, the mowing unit 3 is provided so as to move up and down with the mowing input shaft 38 as a rotation support shaft by the expansion and contraction operation of the lifting cylinder 39. That is, the rear end of the feeder 30 is rotatably supported on the traveling machine body 2 side of the combine 1 with the cutting input shaft 38 as a rotation axis. The feeder 30 constitutes the reaping section 3 together with the cutting blade device 32 and the raking reel 34 provided on the front side thereof. It is configured to move up and down by rotation. 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. The threshing unit 7 includes a handling cylinder 41 provided in a handling room having a handling port 7a opened to the front side, and a receiving net 42 disposed below the handling cylinder 41. The handling cylinder 41 is rotatably supported by a handling cylinder shaft 41a whose axial direction is the front-back direction. The handling cylinder 41 has a cylindrical main body with the handling cylinder axis 41a along the center axis, and spiral blades are provided on the outer peripheral surface of the main body. Above the handling cylinder 41, a plurality of dust valves for adjusting the transport speed (residence time) of thresh in the handling room are provided so as to be adjustable in angle. The receiving net 42 allows the grains to leak, and is provided along the outer peripheral surface of the lower part of the handling cylinder 41.

  The selection unit 8 includes a swing selection plate 43 as a swing unit disposed below the receiving net 42, and a swing shaft 44a that swings the swing selection plate 43 by rotational power from a driving source. It has a mechanism 44, a first conveyor 45, a second conveyor 46, and a Karino 47. In addition, as shown in FIG. 4, a pre-fan 71 is provided in front of the Karino 47, and a second fan 72 is provided behind the Karino 47.

  The swing sorter 43 has a configuration for specific gravity sorting such as a feed pan, a chaff sheave arranged behind the feed pan to adjust the amount of grain leakage, and a Glen sheave arranged below the chaff sheave. The first conveyor 45 is arranged in the first gutter extending in the machine body width direction so as to collect the most grains. The second conveyor 46 is disposed in a second gutter extending in the machine body width direction at a position behind the first conveyor 45 so as to aggregate the second kernels. The Karino 47 blows a sifting wind from the lower front to the upper rear from the swing sorting board 43.

  Further, a reduction conveyor 48 is provided on the left side of the body of the portion where the threshing unit 7 and the sorting unit 8 are disposed. The reduction conveyor 48 has a lower end located near the second conveyor 46 and is connected to the second conveyor 46, and has an upper end located near the front end of the handling drum 41, and extends in an upwardly inclined shape. Has been established. An upper conveyor 49 (see FIG. 4) is provided at the upper end of the reduction conveyor 48 and extends in the left-right direction in front of the handling cylinder 41.

  The combine 1 having the above-described configuration moves the cutting unit 3 to a desired height (harvested crop) with respect to the ground by raising and lowering the feeder 30 around the cutting input shaft 38 (support shaft) in the field. (The cutting height of the cereal stalk), and the working state is changed from the non-working state to the working state, and the vehicle travels in this state. Thus, the combine 1 divides the harvested crop into a target to be cut and a non-cutted target by the left and right weeds 33, 33, and scrapes the pod-bearing portion of the grain stem to be cut by the scraping reel 34. While cutting, the cutting blade device 32 cuts the pods of the grain stem.

  The pods of the grain stalks mowed at the desired mowing position are scraped into the grain header 31 by the rotationally driven scraping auger 37, and are collected near the entrance of the feeder house 35 at the left and right central portions of the grain header 31. Then, it is fed into the handling 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 pods of the grain culm supplied to the threshing unit 7 are subjected to threshing by the threshing unit 7. Specifically, the grain culm supplied to the threshing unit 7 is mainly threshed between the handling cylinder 41 and the receiving net 42 while being transported rearward by the rotating handling cylinder 41. Threshing materials such as grains smaller than the mesh of the receiving net 42 leak from the receiving net 42. Straw chips and the like that do not leak from the receiving net 42 are discharged to the field from the dust outlet provided at the rear of the sorting unit 8 by the transport action of the handling cylinder 41.

  On the other hand, the grain that has been threshed in the threshing unit 7 and has leaked from the receiving net 42 is sorted by the sorting unit 8. Specifically, the thresh that has been threshed by the handling cylinder 41 and leaked from the receiving net 42 is subjected to a specific gravity sorting operation by the rocking sorter 43 and a wind sorting operation by Karino 47 to produce grains such as fines. (First thing), a mixture of grain and straw such as grain with spikes (secondary), and straw waste and the like.

  The grain (first thing) dropped from the swinging sorter 43 by the sorting in the sorting section 8 is conveyed to the Glen tank 10 by a first conveyor 45 and a frying conveyor (not shown) connected to the first conveyor 45. . The second product is returned to the threshing start end side of the handling cylinder 41 by the second conveyor 46 and the reduction conveyor 48 and the upper conveyor 49 connected to the second conveyor 46, and subjected to the threshing process again. Straw chips and the like are discharged to the field through a dust outlet provided at the rear of the sorting unit 8.

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

  The rotational power of the output shaft 25a of the engine 25 is transmitted to the first counter shaft 51 by a first belt transmission mechanism 52 provided between the output shaft 25a 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 engine 25 has a working machine pump shaft that drives a charge pump 54 that operates the lifting cylinder 39 and the like.

  The rotational power transmitted from the output shaft 25a of the engine 25 to the first counter shaft 51 branches 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 reaping unit 3. .

  First, regarding the power transmission system to the threshing unit 7, the rotational power of the first counter shaft 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 for arbitrarily intermittently transmitting the rotational power of the first counter shaft 51 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 handle cylinder shaft 41a via the third belt transmission mechanism 60. Is done. The threshing transmission 58 has a two-stage configuration having a high-speed gear train and a low-speed gear train, and is appropriately controlled by a predetermined actuator under control of a control device provided in the combine 1 according to the type of crop to be processed and the like. The shift operation is performed.

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

  Next, regarding the power transmission system to the traveling section 4, the rotational power of the first counter shaft 51 is transmitted to the second counter shaft 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 continuously variable transmission that employs a method in which hydraulic pressure generated by driving a hydraulic pump is converted back into rotational force by a hydraulic motor. The driving force of the transmission 65 causes the driving sprocket 5 a of the crawler unit 5 constituting the traveling unit 4 to be rotationally driven.

  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 Is transmitted to the second PTO drive shaft 69 via a transmission mechanism 68 including The rotational power of the second PTO drive shaft 69 is transmitted by a predetermined transmission mechanism to a pre-fan shaft 71a for rotating the pre-fan 71, a Kara-min shaft 47a for rotating the Kar-min 47, and a first conveyor shaft 45a for rotating the first conveyor 45. Each is transmitted. The rotational power of the second PTO drive shaft 69 is transmitted to the swing shaft 44a of the swing mechanism 44 via the first conveyor shaft 45a. Further, the rotational power of the first conveyor shaft 45a is transmitted to a second fan shaft 72a for rotating the second fan 72 by a predetermined transmission mechanism.

  The rotational power of the swing 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 a vertical conveyor shaft 48a that rotates the reduction conveyor 48 by a predetermined transmission mechanism, and the rotational power of the vertical conveyor shaft 48a is rotated by the predetermined transmission mechanism to rotate the upper conveyor 49. The power is transmitted to the conveyor shaft 49a.

  Then, regarding the power transmission system to the mowing unit 3, the rotational power of the second PTO drive shaft 69 is transmitted to the mowing input shaft 38 by the seventh belt transmission mechanism 73. The conveyor 36 in the feeder house 35 operates by the rotation drive of the cutting input shaft 38. The seventh belt transmission mechanism 73 is provided with a mowing clutch 75 that transmits the rotational power of the second PTO drive shaft 69 to and from the mowing input shaft 38 arbitrarily. In addition, a pulley 73 a constituting the seventh belt transmission mechanism 73 is fixed to the right end of the cutting input shaft 38.

  The rotation power of the cutting 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 37a that rotates the scraping auger 37 via the second chain transmission mechanism 78. In addition, 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. The rotational power of the PF drive shaft 77 is transmitted to a reel shaft 34b that rotates the scraping reel 34 by a power transmission mechanism including a first reel counter shaft 81 and a second reel counter shaft 82.

  With such a configuration, the driving force of the engine 25 is transmitted to the reaper 3. Then, by operating the work clutch lever 23, the reaping clutch 75 is turned ON / OFF, and the power transmission to the reaping unit 3 is interrupted.

  The combiner 1 according to the present embodiment having the above-described configuration is configured such that the conveyor 36 of the feeder 30 is moved up and down by using the raising and lowering operation of the feeder 30 in order to eliminate clogging of the grain stalk in the feeder 30 as a transport device with a simple structure. Is provided in the conveyor in the reverse direction. That is, the combiner 1 is provided with the feeder 30 in the reaping unit 3, and in a configuration in which the feeder 30 is rotatable up and down about the reaping input shaft 38 as a rotation axis, the feeder 30 is operated by the conveyor reverse operation mechanism. The conveyor 36 is moved in the reverse direction by the elevating operation. Hereinafter, the conveyor reverse operation mechanism will be described with reference to FIGS.

  In the combine 1 according to the present embodiment, the feeder 30 includes a conveyor 36 in a feeder house 35 having a cutting input shaft 38 that receives power transmission in a left-right direction as a drive axis, and a feeder 30. Is provided so as to move up and down by rotation about the reaping input shaft 38 with respect to. That is, as described above, the feeder 30 is provided so as to move up and down around the cutting input shaft 38 by the expansion and contraction operation of the lifting cylinder 39 provided between the feeder house 35 and the body frame 6 (see FIG. 4). (See FIG. 5, arrow A1).

  The feeder house 35 has left and right side portions 91L and 91R, a lower surface portion 92, and an upper surface portion 93, and these surface portions constitute a tubular body having front and rear open ends. Specifically, the upper surface portion 93 has a rear side surface portion 93a and a front side surface portion 93b, each of which has an inclined planar shape, and has a curved surface shape having a front and rear central portion as a top in a side view. Corresponding to the bent surface shape of the upper surface portion 93, the upper portions of the left and right side surface portions 91L and 91R have a mountain shape.

  In such a feeder house 35, at the rear end, a substantially horizontal rectangular opening is formed by the rear end of each of the left and right side portions 91L and 91R, the lower surface 92, and the rear side 93a of the upper surface 93. A part 94 is formed (see FIG. 8). In addition, the front end of the lifting cylinder 39 is rotatably supported by a shaft supporting portion 39a with respect to the front portion of the lower surface portion 92 of the feeder house 35, with the left-right direction being the rotation axis direction.

  The conveyor 36 is a chain conveyor having a chain 95 provided on the left and right sides in parallel in the feeder house 35 and a plurality of plates 96 provided between the left and right chains 95. The plate 96 is provided on the outer peripheral side of the chain 95. The plate 96 is a slender member having a longitudinal direction between the left and right chains 95 in the direction in which it is laid (left-right direction), and is a bent plate-shaped member having a crank-shaped or substantially “U” -shaped 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.

  The conveyor 36 includes a sprocket 97 provided on both the left and right sides of an installation portion of the cutting input shaft 38 as a drive shaft in the feeder house 35 so as to rotate integrally with the cutting input shaft 38. Is wound. On the other hand, a front portion of the chain 95 is wound around a cylindrical front drum 98 provided at a front end in the feeder house 35. The front drum 98 is rotatably supported between a left and right side surface portions 91L and 91R of the feeder house 35 so as to be rotatable around a conveyor driven shaft 98a which is a predetermined rotation axis having a left-right direction as an axial direction. That is, the chain 95 is wound around the sprocket 97 and the front drum 98 endlessly, and the rotation of the sprocket 97 accompanying the rotation of the cutting input shaft 38 moves the plate 96 while maintaining the wound state. Drive. The conveyor 36 is provided so that the rear end of the sprocket 97 protrudes from the rear opening 94 of the feeder house 35 and the front end of the front drum 98 slightly protrudes from the front opening of the feeder house 35. I have.

  With such a configuration, the conveyor 36 is driven in the normal direction by rotating the harvesting input shaft 38 in the counterclockwise direction (the left rotation direction) in the left side view (see FIG. 6, arrow B1) (FIG. 6). , Arrow B2), the cereal stems taken into the feeder house 35 by the scraping auger 37 are hooked on the plate 96, and are conveyed obliquely rearward and upward. That is, when the conveyor 36 is driven in the normal rotation direction, the path portion of the linear chain 95 located below the sprocket 97 and the front drum 98 (the chain 95 located directly above the lower surface 92 of the feeder house 35). The path portion) is a forward path portion moving from the front side to the rear side, and the path portion of the linear chain 95 located above the sprocket 97 and the front drum 98 is a return path portion moving from the rear side to the front side. The grain stalks conveyed by the conveyor 36 are supplied from the feeder house 35 to the threshing unit 7 via the handle 7a (see FIG. 1).

  The reaping input shaft 38 is provided between the left and right side portions 91L and 91R at the rear end of the feeder house 35, and protrudes outward from the left and right side portions 91L and 91R. The reaping input shaft 38 is provided so as to be rotatable relative to the feeder house 35 via a bearing member or the like. Both ends of the cutting input shaft 38 are rotatably supported by support brackets 100 (100L, 100R) provided on the left and right sides of the rear end of the feeder house 35 via bearing members and the like. .

  The support bracket 100 is a member whose longitudinal direction is the vertical direction. The support bracket 100 includes a bent plate-shaped base portion having a substantially “L” shape in plan view formed by the fixed surface portion 101 and the support surface portion 102, and an inner side of the bent shape of the base portion. And a plurality of horizontal plate-shaped rib portions 103 laid on the base plate. The base portion of the support bracket 100 has a fixed surface portion 101 which is a flat plate-shaped portion forming one side in a substantially “L” -shaped plan view shape at a base portion thereof, and also has a substantially “L” -shaped plan view shape. The support surface portion 102, which is a flat plate-shaped portion forming the other side portion in FIG.

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

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

  The support bracket 100 is fixed to the column 105 with the fixing surface 101 in contact with the front surface of the column 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 column 105 by four fastening members 106 arranged at predetermined intervals in the vertical direction.

  As described above, the feeder 30 is supported by the support bracket 100 fixed to the column 105, which is a configuration of the combine 1 on the main unit side, so as to be able to move up and down around the left-right direction as the axial direction. That is, the feeder 30 is provided so as to be vertically lifted and rotated with respect to the machine side with the cutting input shaft 38 as a rotation axis, with the rear end portion being sandwiched between the left and right support brackets 100L and 100R. I have.

  A cutting position sensor 107 for detecting the cutting height (the height of the cutting unit 3 with respect to the machine) based on the rotation angle of the feeder house 35 is provided in front of the upper portion of the left support bracket 100L. The mowing 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 by the machine. The sensor support stay 108 connects the two fastening members via a cylindrical sleeve body 106a that penetrates the upper two fastening members 106 of the four fastening members 106 that fix the support bracket 100L to the main unit side. It is fixedly supported by the member 106.

  The reaping position sensor 107 has a detection piece 107a that is provided rotatably with the left-right direction as the axial direction and protrudes forward. On the other hand, a bar-shaped detection pin 109 acting on the detection piece 107a is protruded from the left side surface portion 91L of the feeder house 35. The detection pin 109 is located above the detection piece 107a, and acts on the detection piece 107a to rotate the detection piece 107a within a predetermined operation range in the elevating operation of the feeder 30. With such a configuration, the mowing position sensor 107 detects the mowing height based on the amount of rotation of the detecting piece 107a that is affected by the detecting pin 109 during the elevating operation of the feeder 30.

  The combiner 1 having the above-described configuration is a conveyor reverse operation mechanism for operating the conveyor 36 of the feeder 30 in the reverse direction by using the raising and lowering operation of the feeder 30, and the raising operation of the feeder 30 is applied to the reaping input shaft 38. The harvesting input shaft 38 is conveyed along with the raising operation of the feeder 30, and is rotated in a direction opposite to the rotation direction (hereinafter, referred to as “normal rotation direction”) when the culm is transported (when the conveyor 36 is driven in the normal rotation direction). A reverse rotation mechanism 110 that rotates in the “reverse direction”). That is, in a state where the feeder 30 is lowered from the rising end position of the lifting operation, the feeder house 35 and the cutting input shaft 38 are engaged by the reversing mechanism 110, and the forward rotation direction of the cutting input shaft 38 with respect to the feeder house 35. Is restricted. By raising the feeder 30 in such a state, the cutting input shaft 38 rotates in the reverse direction together with the feeder house 35.

  According to the reversing mechanism 110, the following operation can be obtained in detail. The reaping 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 relatively rotatable with respect to the feeder house 35. Further, as described later, the gear 120, which is a member of the reverse rotation mechanism 110, is supported by the cutting input shaft 38, and the claw member 130, which is also a member of the reverse rotation mechanism 110, is supported by the feeder house 35 side. ing.

  Therefore, when the feeder 30 is rotated upward about the cutting input shaft 38 while the relative rotation of the cutting input shaft 38 in the normal rotation direction with respect to the feeder house 35 is restricted by the reverse rotation mechanism 110, the feeder 30 is rotated. The cutting input shaft 38 is forcibly rotated in the reverse direction together with the feeder house 35 by the amount of the upward rotation of. That is, the direction of the upward rotation of the feeder house 35 (see the arrow C1 in FIG. 6) is the clockwise direction (the right rotation direction) when viewed from the left side, and the normal rotation direction of the cutting input shaft 38 (see the arrow C2 in FIG. 6). The cutting input shaft 38 engaged with the feeder house 35 by the reverse rotation mechanism 110 rotates in the reverse direction integrally with the feeder house 35 that rotates upward.

  Therefore, the reversing mechanism 110 that rotates the cutting input shaft 38 in the reverse rotation direction by using the raising and lowering operation of the feeder 30 may have any configuration as long as the engagement operation for the cutting input shaft 38 as described above can be obtained. That is, as the reverse rotation mechanism 110, in a configuration in which the cutting input shaft 38 supported on the machine side is relatively rotated with respect to the feeder house 35, the relative rotation of the cutting input shaft 38 is at least relative to the normal rotation direction. What is necessary is just a structure which has the effect | action which controls rotation. Hereinafter, a specific configuration of the reversing mechanism 110 according to the present embodiment will be described.

  As shown in FIGS. 5 to 8, the reversing mechanism 110 is provided on the left side of the combiner 1 in the left-right direction of the main unit, of the left and right 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 outside the combiner 1 in the left-right direction of the machine, and the left side of the rear end of the feeder house 35 is located on the left side. On the other hand, a reversing mechanism 110 is provided.

  The reverse rotation mechanism 110 has a gear 120 as a first engagement member supported by the cutting input shaft 38, and a claw member 130 that engages with the gear 120. The reverse rotation mechanism 110 is configured to include a ratchet mechanism that limits the lifting operation of the feeder 30 that rotates the cutting input shaft 38 via the gear 120 to the lifting operation of the feeder 30.

  The gear 120 is supported by a leftward protruding portion 38 a of the cutting input shaft 38 from inside the feeder house 35. The gear 120 is an annular plate-shaped member through which the cutting input shaft 38 penetrates, and has a plurality of teeth 121 on an outer peripheral side of a main body portion which is an inner peripheral side portion thereof. The teeth 121 have a mountain shape that is substantially triangular when viewed in the rotation axis direction of the gear 120. Between the teeth 121 which are adjacent to each other in the circumferential direction of the gear 120, an engagement concave portion 122 having a substantially “V” shape as viewed in the rotation axis direction of the gear 120 is formed.

  The claw member 130 is provided in a state supported by the feeder 30, and transmits the ascending operation of the feeder 30 to the cutting input shaft 38 via the gear 120 by engaging with the gear 120. 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-shaped member having a predetermined shape portion, and is provided rotatably with the thickness direction being the left-right direction. The claw member 130 has a plate thickness that is substantially the same as or smaller than the gear 120, and is provided at a position in which the position in the left-right direction is substantially the same as the gear 120 so as to be able to engage with the gear 120 ( (See FIG. 7).

  The claw member 130 is provided so as to be rotatable with respect to the left side surface portion 91L of the feeder house 35 constituting the feeder 30. The claw member 130 is rotatably supported by a support shaft 131 protruding leftward from the side surface portion 91L and having the left-right direction as the rotation axis direction.

  The support shaft 131 is a columnar portion, and has a projecting distal end portion as a reduced diameter portion 131a. The reduced diameter portion 131a penetrates the claw member 130, and the retaining ring 135b is formed at the reduced diameter portion 131a via a washer 135a. By receiving the fitting, the pawl member 130 is rotatably supported. Further, the support shaft 131 is supported by a support stay 136 for reinforcement provided between the support shaft 131 and the side surface portion 91L on the lower front side.

  The claw member 130 has a support base 132 that is a support portion of the support shaft 131 and penetrates the support shaft 131, and a claw body 133 that protrudes upward from the support base 132. The support base 132 has a shape protruding around the support shaft 131, and a claw body 133 is provided above the support base 132. The claw body 133 has a shape bent from the upper side of the support base 132 toward the rear side, and has a sharp engagement portion 134 at the tip end thereof, which forms an acute angle toward the rear side where the gear 120 is located. The claw member 130 is engaged with the gear 120 by fitting the sharp engagement portion 134 into the engagement recess 122 of the gear 120. The sharp engaging portion 134 has an outer shape corresponding to the substantially “V” -shaped concave shape of the engaging concave portion 122 so as to fit with the engaging concave portion 122.

  With such a configuration, the claw member 130 rotates clockwise (rightward rotation direction) in a left side view, so that the sharp engagement portion 134 is fitted into the engagement recess 122 located on the front side of the gear 120. And engage with the gear 120. On the other hand, the engagement of the claw member 130 with the gear 120 is released by rotating the claw member 130 engaged with the gear 120 in a counterclockwise direction (counterclockwise rotation) as viewed from the left side.

  The claw member 130 is urged by a spring 140 as an urging member in a direction in which the claw member 130 is engaged with the gear 120, that is, in a clockwise rotation direction (hereinafter referred to as an “engagement direction”) when viewed from the left side. The spring 140 is a tension coil spring, and acts on the claw member 130 to pull the claw member 130 in the engagement direction. The spring 140 is provided on the lower rear side (lower right side in FIG. 10) with respect to the claw member 130, and pulls the rear portion of the claw member 130 downward, thereby engaging the claw member 130 by elastic force. Energize in the direction.

  Specifically, the spring 140 has a hook portion 140a on the upper end, which is one end thereof, and a locking pin 141 that penetrates a portion (right side in FIG. 10) of a portion supported 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 of the locking pin 141 that penetrates the claw member 130 toward the right side (the rear side in FIG. 10).

  On the other hand, the hook 140b at the lower end, which is the other end of the spring 140, is locked to a support stay 142 fixed to the side surface 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 forms a bent plate-like portion having a predetermined bent shape protruding leftward from the side surface portion 91L, and includes a horizontal plate portion 142a along the downward slope of the feeder house 35 and a horizontal plate portion 142a. A vertical plate portion 142b bent upward from the edge portion at right angles to the horizontal plate portion 142a.

  The spring 140 is latched and supported by the support stay 142 in such a state that the lower hook portion 140b is passed through the engagement hole 142c formed in the vertical plate portion 142b. .

  Further, the rotation of the pawl member 130 about the support shaft 131 is operated via an operation wire 145 as a wire member connected to the pawl member 130. One end of the operation wire 145 is connected to the claw member 130 via a connection member 146. The connecting member 146 is an elongated member having a substantially “U” -shaped outer shape that is substantially rectangular when viewed from the side and opened upward when viewed from the front. The upper end of the connecting member 146 is supported by the support shaft 131 of the claw member 130. Is connected to a locking pin 147 that penetrates the front side (left side in FIG. 10). The upper end of the connecting member 146 is connected to a protruding portion of the locking pin 147 that penetrates the claw member 130 to the right side (the rear side in FIG. 10). The locking pin 147 passes through a long hole 146 a formed along the longitudinal direction of the connecting member 146, and is supported by the connecting member 146 through the pin. Thus, the connecting member 146 is provided so as to be relatively movable with respect 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 connecting member 146.

  The operation wire 145 extends through the tubular wire support member 148 fixedly supported on the horizontal plate portion 142a of the support stay 142 and covered with a flexible covering tube 149. The wire support member 148 is fixedly supported by the horizontal plate portion 142a by a fastening action of a nut member or the like in a state of penetrating the horizontal plate portion 142a vertically. The other end of the operation wire 145 is connected to 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. Are linked.

  In the claw member 130, the locking pin 141 for locking the spring 140 to the claw member 130 and the locking pin 147 for connecting the operation wire 145 to the claw member 130 are positioned between the positions supported by the support shaft 131. It is located on the substantially opposite side of the front and rear. That is, the locking pin 141 for the spring 140 is located behind the support shaft 131, and the locking pin 147 for the operation wire 145 is located in front of the support shaft 131.

  Further, between the claw member 130 and the support stay 142, the direction in which the spring 140 is laid (expanding / contracting direction) and the direction in which the operation wire 145 extends are both forwardly inclined substantially vertical directions. The claw member 130 is constantly receiving a downward pulling action by the spring 140, and rotates back and forth about the support shaft 131 like a seesaw depending on the presence or absence of a downward pulling action by the operation wire 145.

  The operation of the reverse rotation mechanism 110 will be described with reference to FIG. Normally, as shown in FIG. 10, the reverse rotation mechanism 110 is not operated, and the claw member 130 moves from the rotation position (hereinafter referred to as “engagement position”) engaging with the gear 120 in a direction opposite to the engagement direction. (Hereinafter, referred to as “anti-engagement direction”). That is, the reverse rotation mechanism 110 is in a non-operation state, and the cutting input shaft 38 is in a non-engagement state with the feeder house 35. The state where the claw member 130 is in the non-engagement position is maintained by the pulling action of the operation wire 145 that pulls the claw member 130 in the anti-engagement direction against the urging action of the spring 140 in the engagement direction.

  Then, by operating a predetermined operating tool that operates the operation wire 145, an operation for bringing the reversing mechanism 110 into an operating state is performed, whereby the pulling action of the claw member 130 by the operation wire 145 is released. As a result, the claw member 130 rotates in the engagement direction by the urging force of the spring 140 (see the arrow D1), the claw member 130 reaches the engagement position, and the sharp engagement portion 134 is located on the front side of the gear 120. The engagement with the engagement recess 122 causes the claw member 130 to engage with the gear 120. That is, the reversing mechanism 110 is activated, and the cutting input shaft 38 is engaged with the feeder house 35.

  The operation wire 145 is pulled by performing an operation for disabling the reverse rotation mechanism 110 by operating a predetermined operation tool from the operation state of the reverse rotation mechanism 110. As a result, the claw member 130 rotates in the anti-engaging direction (the direction opposite to the arrow D1) against the urging force of the spring 140, the engagement of the claw member 130 with the gear 120 is released, and the claw member 130 is disengaged. When the engagement 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, play is provided in the operation direction of the operation wire 145 by the configuration in which the locking pin 147 is engaged with the long hole 146a of the connection member 146. This prevents unintended engagement of the claw member 130 with the gear 120 and the like, and enables the switching operation of the reverse rotation mechanism 110 between the active state and the inactive state.

  Regarding the engagement structure between the gear 120 and the claw member 130, the reversing mechanism 110 is configured to rotate the gear 120 in the reverse direction of the conveyor 36 with respect to the feeder house 35 in a state where the claw member 130 is engaged with the gear 120 (operating state). , That is, a ratchet type structure that allows relative rotation in the right rotation direction when viewed from the left side. That is, each tooth 121 of the gear 120 is set so that the direction of relative rotation of the gear 120 with respect to the feeder house 35 in the operating state of the reverse rotation mechanism 110 is limited to a direction corresponding to the reverse rotation of the cutting input shaft 38. With respect to the circumferential direction of the gear 120, it is inclined to the forward rotation direction side (the left rotation direction side when viewed from the left) of the conveyor 36 with respect to the radial direction of the gear 120.

  According to such a configuration, a state in which the cutting input shaft 38 rotates integrally with the feeder house 35 with the raising / lowering operation of the feeder house 35 occurs due to, for example, a clogging action of the grain stalk in the feeder house 35. In such a case, the following operation can be obtained by bringing the reverse rotation mechanism 110 into the operating state. That is, when the feeder 30 moves upward, the gear 120 rotates in the direction corresponding to the reverse rotation direction of the conveyor 36 (reverse rotation direction) with the ascending feeder house 35. On the other hand, during the lowering operation of the feeder 30, the relative rotation of the gear 120 with respect to the feeder house 35 is allowed. Here, the direction of relative rotation of the gear 120 is the reverse direction. That is, the relative rotation of the gear 120 with respect to the feeder house 35 is allowed during the lowering operation of the feeder house 35, so that the cutting input shaft 38 relatively rotates in the reverse direction with respect to the feeder house 35 via the gear 120. Will be. As described above, according to the ratchet structure including the gear 120 and the claw member 130, the raising and lowering operation of the feeder 30 for rotating the cutting input shaft 38 via the gear 120 is limited to the raising operation of the feeder 30.

  Therefore, in the operating state of the reverse rotation mechanism 110, the gears 120 rotate in the reverse direction relative to the feeder house 35 when the feeder 30 moves up and the feeder house 35 when the feeder 30 descends, respectively. Will be. That is, the action of rotating the cutting input shaft 38 in the reverse direction via the gear 120 is obtained both when the feeder 30 is raised and when the feeder 30 is lowered. For this reason, the feeder 30 repeats the raising and lowering operation, so that the harvesting input shaft 38 is rotated in the reverse direction every time the feeder 30 moves up and down.

  As described above, the reversing mechanism 110 according to the present embodiment includes the gear 120 supported by the cutting input shaft 38 and the claw member 130 urged in the direction (engagement direction) in which the gear 120 is engaged. The feeder 30 includes a ratchet mechanism that restricts the raising and lowering operation of the feeder 30 that rotates the cutting input shaft 38 via the gear 120 to the raising operation of the feeder 30.

  According to the above-described reverse rotation mechanism 110 of the present embodiment, when the reverse rotation mechanism 110 is in the operating state, the feeder 30 rotates upward, and the gear supported by the cutting input shaft 38 by the rotation amount of the feeder 30. With respect to 120, a rotation action in a direction corresponding to the reverse rotation direction of the cutting input shaft 38 is obtained. The rotation action of the gear 120 in the reverse direction is used, and the cutting 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 stalk in the feeder 30 is eliminated.

  Here, for example, when the gear 120 is fixed coaxially to the cutting input shaft 38, that is, when the gear 120 is configured to rotate integrally with the cutting input shaft 38, the gear accompanying the ascent of the feeder 30 is increased. The amount of rotation of the motor 120 in the reverse direction is 1: 1 and transmitted to the reaping input shaft 38, so that 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 elevating operation of the feeder 30 is limited, the clogging of the grain stalk is eliminated with respect to the amount of rotation of the cutting input shaft 38 that operates the conveyor 36 in the reverse direction. Therefore, there is a possibility that a sufficient amount of rotation cannot be obtained.

  Therefore, the combine 1 according to the present embodiment includes an amplifying mechanism 200 that amplifies the amount of rotation of the rotating gear 120 by transmitting the ascent operation of the feeder 30 via the claw member 130 and transmits the amplified amount to the cutting input shaft 38. Prepare. The amplification mechanism 200 will be described with reference to FIGS.

  As shown in FIG. 12, the mowing input shaft 38 is a cylindrical shaft that allows the mowing input shaft 38 to pass through the left side surface portion 91L 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 a support member 201.

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

  In addition, 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 relatively rotatable. The shaft support member 201 penetrates a protruding portion 38 a protruding leftward from the side surface portion 91 </ b> L of the cutting input shaft 38, and can relatively rotate the cutting input shaft 38 via a bearing member 203 fixed to the cutting input shaft 38. I support it. A bearing 204 is interposed between the right end of the shaft support member 201 and the cutting input shaft 38.

  The cutting input shaft 38 has a left end protruding leftward from the support bracket 100L, and supports the gear 120 at the protruding portion 38a. The gear 120 is provided at a position close to the left side with respect to the support bracket 100L. The amplifying mechanism 200 amplifies the amount of rotation of the gear 120 accompanying the elevation of the feeder 30 and transmits the amplified amount to the reaping input shaft 38 when the reversing mechanism 110 is in the operating state.

  The amplifying mechanism 200 includes an input shaft side gear supported by the cutting input shaft 38, an idler shaft 215 as a transmission shaft provided in parallel with the cutting input shaft 38, and meshes with the input shaft side gear supported by the idler shaft 215. And a transmission shaft side gear. In this 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 and a fourth gear 214 as transmission shaft-side gears. It has a third gear 213.

  As shown in FIG. 12, the first gear 211 is provided at a position adjacent to the left side of the gear 120. The first gear 211 is rotatably supported by the cutting input shaft 38 via two bearings 216 and 216 adjacent to each other in the axial direction. The first gear 211 supports the gear 120 penetrating the cutting input shaft 38 coaxially with the axis of the cutting input shaft 38 so as to rotate integrally with the gear 120.

  The first gear 211 has a support tubular portion 211a that projects from the right side of the outer peripheral surface of the reaping input shaft 38 at a predetermined interval. The first gear 211 is fixed to the gear 120 by a fixing bolt 217 in a state where the support cylinder portion 211a is inserted into the inner peripheral hole 120a of the gear 120 from the left side. The fixing bolt 217 passes through a bolt hole 211b formed in the first gear 211 from the left side and is screwed into the main body of the gear 120. The fixing portions by the fixing bolts 217 are provided at a plurality of positions (six in the present embodiment) at equal intervals around the axis of the cutting input shaft 38. The first gear 211 has substantially the same outer diameter as the gear 120.

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

  The right end, which is one end 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 of the idler shaft 215, is supported by a lower portion of a bridge support plate 220 that supports the left end of the cutting input shaft 38.

  The bridging support plate 220 has a short cylindrical bearing support portion 220a at the lower portion thereof with the left-right direction as the cylinder axis direction. The left end of the idler shaft 215 is provided in the bearing support portion 220a via a bearing 221. The part is rotatably supported. The erection support plate 220 is a plate-shaped member having a substantially chamfered rectangular outer shape whose longitudinal direction is the vertical direction in a side view, and supports the left ends of the cutting input shaft 38 and the idler shaft 215, respectively. These shafts are provided between the left ends of the shafts.

  In the idler shaft 215, a second gear 212 meshing with the first gear 211 is provided 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 has a smaller diameter than the first gear 211, and functions as a pinion with respect to the first gear 211.

  In the present embodiment, the first gear 211 has 38 teeth, and the second gear 212 has 19 teeth. In other words, the gear ratio between the first gear 211 and the second gear 212 is １ ／, and the transmission ratio of the rotation from the first gear 211 to the second gear 212 is two.

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

  A fourth gear 214 meshing with the third gear 213 is provided at a position corresponding to the third gear 213 in the axial direction of the cutting 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 on the outer peripheral surface of the cutting input shaft 38 and the inner peripheral surface of the fourth gear 214 along the axial direction of the cutting input shaft 38. The input shaft 38 is not rotatable relative to the input shaft 38, and rotates integrally with the cutting input shaft 38. The fourth gear 214 has a smaller diameter than the third gear 213, and functions as a pinion with respect to the third gear 213.

  In the present embodiment, the fourth gear 214 has 19 teeth, while the third gear 213 has 38 teeth. In other words, the gear ratio between the third gear 213 and the fourth gear 214 is 、, and the transmission ratio of the rotation from the third gear 213 to the fourth gear 214 is two.

  The left end of the cutting input shaft 38 is supported on the upper part of the bridge support plate 220 via a fourth gear 214. The fourth gear 214 has a cylindrical support cylinder portion 214a through which the cutting input shaft 38 passes along with the main body portion, on the left side of the main body portion on which teeth engaging with the third gear 213 are formed on the outer peripheral side. On the other hand, the bridging support plate 220 has a short cylindrical bearing support portion 220b having a left-right direction as a cylinder axis direction at an upper portion thereof, and a fourth gear 214 of the fourth gear 214 via a bearing 223 in the bearing support portion 220b. The support cylinder 214a is rotatably supported. That is, the left end of the reaping input shaft 38 is rotatably supported on the upper part of the bridge supporting plate 220 via the fourth gear 214 and the bearing 223.

  The cutting input shaft 38 has a left end on which the male screw portion 38b is formed protruding leftward from the erection support plate 220. The protruding portion of the mowing input shaft 38 protruding from the erection support plate 220 receives the nut 255 screwed into the male screw portion 38b via a locking portion 224 made of a washer, a retaining ring, or the like penetrating the mowing input shaft 38. Supported.

  According to the amplification mechanism 200 described above, in the operating state of the reverse rotation mechanism 110, the rotation of the gear 120 that rotates in the reverse rotation direction by receiving the transmission of the upward movement of the feeder 30 via the claw member 130 rotates the gear 120. As a result, the rotation of the first gear 211 that rotates relative to the reaping input shaft 38 becomes integral. The rotation of the first gear 211 is transmitted to the idler shaft 215 via the second gear 212 meshing with the first gear 211. Here, the amount of rotation of the first gear 211 is increased and transmitted to the idler shaft 215 according to the speed increase ratio of the first gear 211 and the second gear 212. In the present embodiment, as described above, the speed increase 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 cutting 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, the amount of rotation of the third gear 213 is increased and transmitted to the fourth gear 214 due to the speed increase ratio of the third gear 213 and the fourth gear 214. Since the fourth gear 214 rotates integrally with the cutting input shaft 38, the amount of rotation of the fourth gear 214 becomes the amount of rotation of the cutting input shaft 38 as it is. In the present embodiment, as described above, the speed increase 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 cutting input shaft is driven via the fourth gear 214. 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 performed by the first gear 211 → the second gear 212 → the idler shaft 215 → the third gear. The speed is increased by the flow of the gear 213 → the fourth gear 214 → the cutting input shaft 38, and transmitted as the rotation of the cutting input shaft 38 in the reverse rotation direction. In the present embodiment, the rotation amount of the gear 120 is increased in two stages by the speed increase ratio between the first gear 211 and the second gear 212 and the speed increase ratio between the third gear 213 and the fourth gear 214. The rotation is quadrupled and transmitted to the cutting input shaft 38. The number of gears, the number of teeth of each gear, the speed increase ratio between gears, and the like in the amplification mechanism 200 are not particularly limited to the configuration of the present embodiment.

  In the amplifying mechanism 200, as described above, the erection support plate 220 that supports the left end of each of the cutting input shaft 38 and the idler shaft 215 has a support that is formed to be bent substantially inward (to the right) at the rear thereof. It has a surface part 220c. In other words, the erection support plate 220 is a portion that supports the left end of each of the cutting input shaft 38 and the idler shaft 215, and has a plate-shaped plate main body 220d whose left and right direction is a plate thickness direction, And a plate-shaped support surface portion 220c having a direction, and has a substantially “L” shape in plan view.

  The erection support plate 220 is provided so that the support surface portion 220c contacts or substantially contacts the front side of the left support 105L on the main unit side. In the erection support plate 220, the rear support surface portion 220c uses the rear surface 220e as a contact surface with the front surface of the left column 105L and serves as a support portion for the column 105L.

  That is, in the operating state of the reverse rotation mechanism 110, the cutting input shaft 38 receives an action from the front side to the rear side via the claw member 130 and the gear 120 as the feeder 30 is raised. That is, the cutting input shaft 38 tries to escape backward. Therefore, the rearward movement of the reaping input shaft 38 is restricted by using the support surface portion 220c of the erection support plate 220 that supports the left end portion of the reaping input shaft 38 as a supporting portion for the column 105L. Escape is prevented. Accordingly, a stable engagement state of the engagement of the claw member 130 with the gear 120 can be obtained.

  Further, in the amplification mechanism 200, the mowing input shaft 38 and the idler shaft 215 are generated by the reaction force of the engagement between the input shaft side gear supported by the mowing input shaft 38 and the transmission shaft side gear supported by the idler shaft 215. In the direction in which the axes are separated from each other. Therefore, a construction is adopted in which the erection support plate 220 is provided between the cutting input shaft 38 and the idler shaft 215 in an erected state, and the left end of each shaft is supported by the erection support plate 220.

  According to such a configuration, the center distance between the cutting input shaft 38 and the idler shaft 215 is kept constant. Accordingly, the input shaft side gear and the transmission shaft side gear constituting the amplifying mechanism 200 are restricted from being separated from each other, and a stable meshing state of the gears can be obtained.

  As described above, according to the erection support plate 220, a stable operation state can be obtained in the reversing mechanism 110 and the amplifying mechanism 200, and the reversing action of the conveyor 36 by the reversing mechanism 110 and the increase in the rotation by the amplifying mechanism 200 are increased. It is possible to reliably obtain the speed transmission action.

  Subsequently, a configuration related to an operation of the reverse rotation mechanism 110 in the combine 1 according to the present embodiment will be described.

  The operation of the reverse rotation mechanism 110 is operated by a predetermined operation tool via the operation wire 145 as described above. In the present embodiment, as the operating tool of the reversing mechanism 110, a work clutch lever 23 provided in the operation unit 15 for turning on and off the threshing clutch 57 and the reaping clutch 75 (see FIG. 4) is employed.

  That is, the combine 1 of the present embodiment is configured such that the operation and non-operation of the reverse rotation mechanism 110 are operated by operating the work clutch lever 23 which is a work operation tool for operating the reaping unit 3 and the threshing unit 7. It is configured. Therefore, the other end of the operation wire 145 is connected via a component of the link mechanism 300 provided between the claw member 130 and the work clutch lever 23 so that the reverse rotation mechanism 110 is operated by the work clutch lever 23. It is connected to the work clutch lever 23. That is, the claw member 130 is linked to the work 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 reverse rotation mechanism 110 will be described with reference to FIGS. 14 and 15. As shown in FIG. 14, the work clutch lever 23 has a rod-shaped lever body 23a having a predetermined shape, and a substantially spherical grip 23b provided at an upper end of the lever body 23a.

  The work clutch lever 23 is provided so as to protrude upward from a lever guide 150 provided on a lever column 24 provided on the left side of the driver's seat 17. The lever guide section 150 is provided with the work clutch lever 23 along a predetermined operation movement path having a plurality of operation positions corresponding to predetermined operation contents as stop positions in a state where the lever main body section 23a of the work clutch lever 23 is penetrated. Guide movement. The lever main body 23a has a predetermined bent shape so as to extend upward from the lever column 24 to the right side on the driver seat 17 side.

  The lever guide 150 has a guide opening 151 formed in 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 work clutch lever 23. The guide plate 152 has a rectangular outer shape in plan view. The guide plate 152 has a plate opening that is smaller than the opening size of the guide opening 151 so as to be included in the opening range of the guide opening 151 in plan view, and that has an opening shape along the opening shape of the guide opening 151. A portion 152a is formed. The plate opening 152a is covered with an elastically deformable plate-shaped covering member 153. The covering member 153 has an opening through which the lever main body 23a of the work clutch lever 23 penetrates. The opening of the covering member 153 includes a slit-shaped portion along the movement path of the work clutch lever 23 and a wide portion such as a substantially circular shape at each operation position of the work clutch lever 23.

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

  The work clutch lever 23 is provided at a corner portion of the lever guide portion 150 between the first movement route portion 161 and the third movement route portion 163 and a corner portion of the first movement route portion 161 and the second movement route portion 162. The portion, the front end portion of the second movement route portion 162, and the rear end portion of the third movement route portion 163 are set as operation positions corresponding to predetermined operation contents. The details are as follows.

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

  The stop operation position P0 is an operation position where the transmission of power to the mowing unit 3 and the threshing unit 7 is turned off, and the reverse rotation mechanism 110 is turned off. That is, in the state where the work clutch lever 23 is at the stop operation position P0 (see FIG. 15A), the cutting clutch 75 and the threshing clutch 57 (see FIG. 4) are in the OFF state, and the claw member 130 in the reverse rotation mechanism 110. Is located at the disengaged position, and the reaping input shaft 38 is disengaged from the feeder house 35. That is, the state where the work clutch lever 23 is located at the stop operation position P0 is a so-called neutral state. In the present embodiment, on the surface of the lever column 24, near the stop operation position P0, there is provided a stop display section 170 displaying the word "OFF".

  The first work operation position P1 is a position moved by a predetermined amount to the right, which is the first direction, from the stop operation position P0, and is an operation position where transmission of power to the threshing unit 7 is in an on state. That is, in the state where the work clutch lever 23 is in the first work operation position P1 (see FIG. 15B), the cutting clutch 75 is in the OFF state, the threshing clutch 57 is in the ON state, and the reverse rotation mechanism 110 is in the inoperative state. Yes, the threshing unit 7 is in operation. In the present embodiment, on the surface of the lever column 24, near the first work operation position P1, there is provided a threshing display section 171 that displays the character "Koku".

  The second work operation position P2 is a position that is moved from the first work operation position P1 by a predetermined amount in the forward direction, which is the third direction, and while the power transmission to the threshing unit 7 is maintained, the harvesting is performed. This is an operation position where the transmission of power to the unit 3 is in an on state. That is, in the state where the work clutch lever 23 is in the second work operation position P2 (see FIG. 15C), the cutting clutch 75 and the threshing clutch 57 are in the ON state, the reverse rotation mechanism 110 is in the non-operating state, and the cutting section 3 and the threshing unit 7 are in operation. In the present embodiment, on the surface of the lever column 24, near the second work operation position P2, there is provided a reaping display section 172 displaying the characters "reap".

  The reverse rotation operation position P3 is a position that has been moved from the stop operation position P0 by a predetermined amount in a backward direction, which is a second direction different from the first direction, by a predetermined amount, and is an operation position where the reverse rotation mechanism 110 is operated. That is, in the state where the work clutch lever 23 is in the reverse operation position P3 (see FIG. 15D), the cutting clutch 75 and the threshing clutch 57 are in the OFF state, and in the reverse rotation mechanism 110, the claw member 130 is in the engagement position. And the cutting input shaft 38 is engaged with the feeder house 35. In the present embodiment, on the surface of the lever column 24, near the reversing operation position P3, there is provided a reversing reversing display portion 173 displaying the text "Cleaning reversal".

  As described above, in the combine 1 according to the present embodiment, the work clutch lever 23 is at a position moved at least a predetermined amount from the stop operation position P0 in the first direction, and at least one of the reaping unit 3 and the threshing unit 7. There are a first work operation position P1 and a second work operation position P2 as work operation positions in which the transmission of power to the vehicle is in the on state. In other words, the first work operation position P1 is a position moved by a predetermined amount in the first direction (rightward) from the stop operation position P0, and is a work operation position where transmission of power to the threshing unit 7 is in an on state. The second work operation position P2 is a position moved by a predetermined amount in the rightward and forward directions from the stop operation position P0, and is a work operation position in which transmission of power to the threshing unit 7 and the reaping unit 3 is in an on state. It is.

  In the present embodiment, the second direction, which is the moving operation direction of the work clutch lever 23 from the stop operation position P0 to the reverse rotation operation position P3, is the movement from the first work operation position P1 to the second work operation position P2. The direction 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 front direction, and the opposite rear direction is the second direction.

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

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

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

  The supported portion 23c of the work clutch lever 23 is supported below the right plate surface of the plate portion 311 along the substantially mountain-shaped bottom of the plate portion 311. The supported portion 23c is fixed at a predetermined position with the second rotation axis S2 coinciding with the central axis of the supported portion 23c as a rotation axis direction by an annular or cylindrical support member 313 fixed to the plate portion 311. It is rotatably supported.

  As described above, the work clutch lever 23 is rotatable in the front-rear direction about the first rotation axis S1 along the left-right direction by the lever support rotation plate 310, and is also rotated in the front-rear direction in plan view. It is supported so as to be rotatable in the left-right direction about the dynamic axis S2. Then, in relation to the above-described operation movement path of the work clutch lever 23, the movement of the second movement path section 162 and the third movement path section 163 along the front-rear direction includes the rotation of the work clutch lever 23 in the front-rear direction. An operation is used, and a rotation operation in the left-right direction is used for the movement of the first movement path section 161 along the left-right direction (see FIG. 14).

  The rotation arm body 320 includes a support shaft portion 323 that rotates about a third rotation axis S3 along the left-right direction, and a rearward portion from the right end, which is one side of the support shaft portion 323 in the axial direction. It has a first arm 321 that extends, and a second arm 322 that extends downward from the left end on the other axial side of the support shaft 323. The first arm 321 and the second arm 322 are integrally connected to each other via a support shaft 323, and have a substantially “L” shape in a side view as viewed in the axial direction of the third rotation shaft S3. It rotates integrally about the three rotation axis S3. The support shaft 323 is supported at a predetermined position with respect to a predetermined frame member arranged in the lever column 24. As described above, the rotating arm body 320 is provided to be rotatable around the third rotating shaft S3 at a fixed position in the lever column 24.

  The first arm 321 is a long plate-like member, and is fixed to the right end of the support shaft 323 in a direction in which the left-right direction is the plate thickness direction. An elongated hole 321a is formed at the rear of the first arm 321 along the longitudinal direction of the first arm 321. A rod-shaped engaging pin 314 protruding rightward from a lower front portion of the plate portion 311 penetrates 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 rotation arm body 320 is engaged with the lever support rotation plate 310 by passing the engagement pin 314 through the long hole 321a of the first arm 321. The engagement between the long hole 321 a and the engagement pin 314 maintains the engagement state between the lever support rotation plate 310 and the rotation arm body 320, and accompanies the rotation of the plate portion 311 and the first arm 321. The 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 long plate-like member, and is fixed to the left end of the support shaft 323 in a direction in which the left-right direction is the plate thickness direction. The other end of the operation wire 145 is connected to an intermediate portion of the second arm 322. At the other end of the operation wire 145, a rod-shaped connecting member 324 is provided. On the other hand, a rod-shaped connecting pin 325 is provided at an intermediate portion of the second arm 322 so as to protrude leftward. The connecting pin 325 penetrates the distal end of the connecting member 324. The connecting member 324 is locked and supported by the connecting pin 325, for example, by penetrating the locking pin through the tip of the connecting pin 325 that has passed through the connecting member 324. Thus, the other end of the operation wire 145 is connected to the second arm 322 of the rotating arm body 320.

  The other end side of the operation wire 145 extends through the wire support column 331 arranged in the lever column 24 via the support stay 332 so as to extend horizontally substantially rearward from the connection end to the second arm 322. Supported. The support stay 332 is a bent plate-like member having a substantially “U” shape in a side view, and is fixed to the wire support column 331 by welding or the like in a direction in which the bottom side in the substantially “U” shape is the front side. ing. In addition, a wire support member 333 that allows the operation wire 145 to pass therethrough is provided at the other end of the coating tube 149 that covers the operation wire 145. The wire support member 333 is fixed to the support stay 332 so as to penetrate the front part of the support stay 332.

  As described above, the portion on the other end side of the operation wire 145 substantially regulates the direction of the operation force (tensile force) with respect to the operation wire 145 and is substantially front and rear so that the operation force acts on the operation wire 145 stably. It is supported horizontally along the direction. More specifically, the forward extension of the operation wire 145 from the wire support member 333 is slightly inclined leftward and forward (see FIG. 17). With such a connection structure of the operation wire 145 to the rotation arm body 320, the second arm 322 is moved forward by the rotation of the rotation arm body 320 about the third rotation axis S3, so that the operation wire 145 will be pulled forward from the other end.

  The work clutch lever 23 that operates the link mechanism 300 having the above-described configuration is provided with a plurality of switches that are operated by the operation of a predetermined member that is linked to the operation of the work clutch lever 23. The plurality of switches include a threshing switch 401, a mowing switch 402, and a reverse switch 403. These switches function as detection means for detecting the operation position of the work clutch lever 23, and are connected to a controller 400 as a control unit included in the combine 1, as shown in FIG.

  The controller 400 connects various functional units such as a CPU (Central Processing Unit) that executes various arithmetic processes and controls, a ROM (read only memory) as a storage unit, a RAM (random access memory), and an input / output interface via a bus or the like. It is provided with the configuration that was made. The CPU performs arithmetic processing according to various programs stored in a ROM or the like. The controller 400 receives detection signals from the threshing switch 401, the mowing switch 402, and the reverse switch 403, and detection signals from various sensors included in the combine 1, and generates a control signal based on these input signals.

  The 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 through the operation control of the threshing clutch actuator based on the detection signal from the threshing switch 401. The cutting clutch 75 is connected to the controller 400 via a cutting clutch actuator (not shown). The controller 400 controls the operation of the cutting clutch 75 through the operation control of the actuator for the cutting clutch based on the detection signal from the cutting switch 402. The detection signal from the reverse rotation switch 403 is used for start / stop control of the engine 25 described later performed by the controller 400.

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

  As shown in FIG. 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 oriented such that the push button 401a side is the rear side, and is located on the left side of the front-rear extension frame 341 arranged in the lever column 24 along the front-rear direction at the position on the left side of the work clutch lever 23 in a plan view. 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 work clutch lever 23, a pressing member 350 that presses the push button 401a in conjunction with the movement operation of the work clutch lever 23 is provided. The pressing member 350 includes a cylindrical shaft support 351 whose vertical direction is the cylindrical axis direction, an engagement arm piece 352 provided on the front side of the shaft support 351 and engaging with the work clutch lever 23, and a left side from the shaft support 351. And a pressing arm piece 353 that presses against the push button 401a.

  The pressing member 350 coaxially supports the shaft support 351 with respect to a support column 354 provided on the rear side of the work clutch lever 23 in the lever column 24, and coincides with the center axis of the cylindrical shaft support 351. It is provided so as to rotate about a fourth rotation axis S4 along the vertical direction. The support column 354 is fixed by welding or the like to the rear side of a horizontal frame 344 installed between the front and rear extension frame 341 and the right and front extension frame 343 disposed on the right side in parallel with the support frame 341 in the lever column 24. Has been established. The engagement arm piece 352 and the pressing arm piece 353 constitute an integral pressing member 350 together with the shaft support 351 and rotate about the fourth rotation axis S4.

  The engagement arm piece 352 is a plate-shaped portion having the vertical direction as the plate thickness direction, and has a concave portion 352a whose front side is bifurcated and whose front side is an open side. The pressing member 350 engages with the work clutch lever 23 by positioning the lever main body 23a in the concave portion 352a of the engaging arm piece 352.

  The pressing arm piece 353 is a plate-shaped part having a thickness direction substantially in the front-rear direction, and is provided such that the distal end is located in front of the push button 401a. The front plate surface 353a of the pressing arm piece 353 serves as a pressing surface, and presses the push button 401a.

  With such a configuration, the left and right rotation of the work clutch lever 23 about the second rotation axis S2 is performed about the fourth rotation axis S4 of the pressing member 350 via the engagement arm piece 352. It is transmitted as rotation in the left-right direction. The thrusting switch 401 is switched ON / OFF by the forward and backward movement of the pressing arm piece 353 due to the rotation of the pressing member 350. That is, when the work clutch lever 23 is moved rightward from the stop operation position P0 toward the first work operation position P1, the pressing member 350 is rotated clockwise in the clockwise direction in plan view. Accordingly, 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 when the work clutch lever 23 moves from the first work operation position P1 to the second work operation position P2. On the other hand, by returning the work 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 on the push button 401a is released with the rotation of the pressing member 350, and the threshing switch 401 Is turned off.

  The reaper switch 402 is a detection device for detecting that the work clutch lever 23 is at the second work operation position P2, which is a position corresponding to reaping “on”. Specifically, the mowing 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 mowing switch 402 is a lever switch having a rotating lever 402a that rotates around a predetermined rotating shaft. When the turning lever 402a rotates a predetermined amount from the OFF state, It will be in the ON state. The reaper switch 402 is configured such that the rotation lever 402a is projected upward and the rotation axis direction of the rotation lever 402a is in the left-right direction, and is horizontal in the lever column 24 at a position below the lever support rotation plate 310. It is fixedly supported at a predetermined position by a fixing tool such as a bolt on a switch support stay 345 provided in the shape.

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

  With such a configuration, mowing is performed by the forward and backward movement of the first lever operation arm 371 accompanying the rotation of the lever support rotation plate 310 due to the forward and backward rotation of the work clutch lever 23 about the first rotation axis S1. ON / OFF of the switch 402 is switched. That is, by operating the work clutch lever 23 in the forward direction from the first work operation position P1 toward the second work operation position P2, the plate portion 311 rotates clockwise (clockwise) in a right side view. Then, along with this, the horizontal shaft portion 371a of the first lever operation arm 371 moves rearward and presses the rotation lever 402a to rotate rearward, so that the mowing 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 operation is released, and the mowing switch 402 is turned off.

  The reverse rotation switch 403 is a detection device for detecting that the work clutch lever 23 is at a reverse rotation operation position P3 which is a position corresponding to the mowing 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 rotation operation position P3.

  The reversing switch 403 is a lever switch having a rotating lever 403a that rotates about a predetermined rotating shaft, similarly to the mowing switch 402, and is turned on when the rotating lever 403a rotates a predetermined amount from the OFF state. State. The reversing switch 403 is configured to protrude the rotating lever 403a upward, and to rotate the rotating axis of the rotating lever 403a in the left-right direction. Is 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 operation arm 372 is a rod-shaped portion bent in an L-shape. The second lever operation arm 372 is fixed to a lower side of a left bent surface portion 322 a provided at a lower end portion of the second arm 322 by welding or the like and extends downward. It has a horizontal shaft portion 372a that is bent rightward and extends in the bar axis direction in the left-right direction at its extending end. The second lever operation arm 372 positions the horizontal shaft portion 372a on the front side of the rotation lever 403a of the reverse rotation switch 403.

  With such a configuration, the second lever operation associated with the rotation of the rotation arm body 320 via the lever support rotation plate 310 due to the rotation of the work clutch lever 23 in the front-rear direction about the first rotation axis S1. The forward / backward movement of the arm 372 switches ON / OFF of the reverse switch 403. That is, when the work clutch lever 23 is moved backward from the stop operation position P0 toward the reverse rotation operation position P3, the plate portion 311 is rotated in the left rotation direction (counterclockwise) in a right side view. The rotation arm body 320 rotates in the right rotation direction when viewed from the right side in conjunction with the rotation of the second lever operation arm 372, whereby the horizontal shaft portion 372a of the second lever operation arm 372 moves rearward to press the rotation lever 403a. To rotate backward, and the reverse switch 403 is turned on. On the other hand, when the work clutch lever 23 is returned from the reverse rotation operation position P3 to the stop operation position P0, the rotation of the lever support rotation plate 310 and the rotation arm body 320 causes the rotation lever 403a of the second lever operation arm 372 to rotate. Is released, and the reverse rotation switch 403 is turned off.

  An example of an operation mode of the combine 1 having the above configuration will be described with reference to FIGS. 15, 18, 19, and 20.

  First, a 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. 15A and 19B, the work clutch lever 23 is located at the neutral position in the front-rear direction and 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 mowing 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. 20B, the reverse rotation mechanism 110 is in a non-operating state, and the claw member 130 is located at the non-engaging position. The state in which the claw member 130 is in the non-engagement position is a state in which the rotary arm body is at a predetermined rotation position via the lever support rotation plate 310 corresponding to the work clutch lever 23 held at the neutral position in the front-rear direction. It is held by the pulling action of the operation wire 145 against the urging action of the spring 140 by the spring 320. The state where the work clutch lever 23 is located at each operation position is held by an appropriate structure such as a connection support structure of each member in the link mechanism 300 or a predetermined holding structure separately provided.

  When the work is started from the neutral state, the work clutch lever 23 is moved rightward from the stop operation position P0 toward the first work operation position P1 as shown in FIG. 15B (see arrow X1). . As a result, the pressing member 350 engaged with the work clutch lever 23 is rotated clockwise about the fourth rotation axis S4 in the plan view (see arrow M1 in FIG. 17), and the threshing switch is pressed by the pressing arm piece 353. The push button 401a of 401 is pressed, and 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 the detection signal from the threshing switch 401 is input to the controller 400, the controller 400 sends a control signal to the threshing clutch actuator to set the threshing clutch 57 to the “on” state. As a result, the threshing clutch 57 is turned ON, the threshing unit 7 starts operating, and the handling cylinder 41 and the like start rotating.

  In a state where the work clutch lever 23 is at the first work operation position P1, the reverse rotation mechanism 110 is in an inactive state as in the neutral state (see FIG. 20B). This is based on the fact that the work clutch lever 23 is in the neutral position in the front-rear direction regardless of whether the work clutch lever 23 is in the stop operation position P0 or the first work operation position P1.

  Next, as shown in FIG. 15C, the work clutch lever 23 is operated to move forward from the first work operation position P1 toward the second work operation position P2 (see arrow X2). As a result, the lever support rotation plate 310 rotates clockwise about the first rotation axis S1 when viewed from the right side (see arrow M2 in FIG. 19C), and the first lever operation arm 371 cuts off. The turning lever 402a of the switch 402 is pressed and turned (see the arrow M3 in FIG. 19C), and the mowing switch 402 is turned on. Thereby, it is detected that the work clutch lever 23 is at the second work operation position P2. Here, since the position of the work clutch lever 23 in the left-right direction is constant between the first work operation position P1 and the second work operation position P2, the rotation of the pressing member 350 for turning on the threshing switch 401 is set. In the state where the moving position is held, the forward movement of the work clutch lever 23 is allowed by the concave portion 352a of the engagement arm piece 352.

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

  Then, when clogging of the grain stalk occurs in the feeder 30 during the operation by the combine 1, as shown in FIG. 15D, the operation clutch lever 23 is moved from the second operation operation position P2 to the reverse rotation operation position P3. Is operated. Thereby, the operation of the cutting unit 3 and the threshing unit 7 is stopped, and the reversing mechanism 110 is activated.

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

  That is, in the first stage, the action of the first lever operating arm 371 on the cutting switch 402 is released by turning the lever support turning plate 310 in the left rotation direction as viewed from the right side, and the cutting switch 402 is turned off to set the cutting clutch. This is a rearward operation from the second work operation position P2 to the first work operation position P1 in which the state 75 is set to the "off" state (see the arrow X3 in FIG. 15D). In the second stage, the pressing member 350 is rotated in the counterclockwise direction in plan view to release the action of the pressing arm piece 353 on the threshing switch 401, the threshing switch 401 is turned off, and the threshing clutch 57 is turned off. This is a leftward operation from the first work operation position P1 to the stop operation position P0 (see arrow X4 in FIG. 15D). The third stage is a backward operation from the stop operation position P0 to the reverse rotation operation position P3 in which the harvest reverse rotation is turned ON (see the arrow X5 in FIG. 15D).

  When the work clutch lever 23 is at the stop operation position P0 and the neutral state is used as a reference, the reverse rotation mechanism 110 is activated by operating the work clutch lever 23 backward from the neutral state. Here, the OFF state of the threshing switch 401 is maintained. That is, since the position of the work clutch lever 23 in the left-right direction is constant between the stop operation position P0 and the reverse rotation operation position P3, the turning position of the pressing member 350 that sets the threshing switch 401 to the OFF state is held. In this state, the rearward movement of the work clutch lever 23 is allowed by the concave portion 352a of the engagement arm piece 352.

  When the work clutch lever 23 is moved from the stop operation position P0 to the reverse rotation operation position P3, as shown in FIG. 19A, the lever support rotation plate 310 is moved rightward with respect to the first rotation axis S1. The first arm 321 is rotated leftward when viewed (see arrow M4), and in conjunction with this, the first arm 321 is pushed upward by the engagement pin 314 penetrating the long hole 321a, and the rotating arm body 320 is moved to the third position. It turns rightward in the right side view about the turning axis S3 (see arrow M5). Thereby, 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 at the disengaged position is released. As a result, as shown in FIG. 20A, the pawl member 130 rotates in the engaging direction and engages with the gear 120 by the urging force of the spring 140 (see arrow M6), and the reaping input shaft 38 is moved to the feeder house. 35 is engaged.

  As described above, the link mechanism 300 releases the tension of the operation wire 145 against the urging force of the spring 140 with respect to the claw member 130 by the stroke operation of the work clutch lever 23 from the stop operation position P0 to the reverse rotation operation position P3. Is configured. In other words, the link mechanism 300 disengages the pawl member 130 from the engagement position against the urging force of the spring 140 by the stroke operation of the work clutch lever 23 from the reverse rotation operation position P3 to the stop operation position P0. The operation wire 145 that is moved to and held at the position is configured to obtain a pulling action.

  When the feeder 30 moves upward in the operation state of the reverse rotation mechanism 110, that is, in a state where the cutting input shaft 38 is engaged with the feeder house 35, the cutting input shaft 38 rotates in the reverse direction, and the conveyor in the feeder 30 is rotated. 36 will operate in the opposite direction. Thereby, clogging of the grain stalk in the feeder 30 is eliminated.

  Here, when the clogging of the grain stem in the feeder 30 is eliminated, the raising operation of the feeder 30 may be performed a plurality of times as necessary by lowering the feeder 30 again. When the feeder 30 descends in the operation state of the reverse rotation mechanism 110, the ratchet structure of the reverse rotation mechanism 110 allows the feeder house 35 to rotate relative to the cutting input shaft 38, and moves the cutting input shaft 38 in the normal rotation direction. Is prevented or suppressed.

  After the clogging of the grain culm in the feeder 30 is resolved, the combine clutch 1 is moved to the first work operation position P1 and the second work operation position P2 again to move the combine 1 into the work state, and the work is resumed. Is done.

  In the operation interlocking mechanism of the work clutch lever 23 and the reverse rotation mechanism 110 as described above, the pawl member 130 of the reverse rotation mechanism 110 is engaged with the gear 120 by the link mechanism 300 in accordance with the operation of the work clutch lever 23. It is rotated in the anti-engaging direction in two steps from the mating position. In other words, the claw member 130 is located at the disengagement position where the engagement with the gear 120 is released as the non-engagement position, and is movable from the disengagement position to the retreat position rotated further in the anti-engagement direction. It is configured. The details are as follows.

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

  As shown in FIG. 19A, in a state where the work clutch lever 23 is at the rear position (reverse operation position P3), the pawl member 130 engages with the gear 120 as shown in FIG. , And the reversing mechanism 110 is in the operating state.

  When the work clutch lever 23 is operated from the rear position to the neutral position (the stop operation position P0 or the first work operation position P1), as shown in FIG. 19B, the lever support rotation plate 310 is viewed from the right side. To rotate rightward (see arrow M7), and in conjunction therewith, the rotating arm body 320 rotates leftward as viewed from the right (see arrow M8), and the other end of the operation wire 145 is It is pulled forward (see arrow M9). Thereby, as shown in FIG. 20B, the pawl member 130 rotates in the anti-engaging direction against the urging force of the spring 140 to reach the disengaged position (see arrow M10), and the reverse rotation mechanism 110 Becomes inactive.

  Further, as shown in FIG. 19C, when the work clutch lever 23 is operated from the first work operation position P1, which is the neutral position, to the front position (the second work operation position P2), the lever support rotation plate is moved. Reference numeral 310 further pivots clockwise in the right side view (see arrow M2), and in conjunction with this, the first arm 321 is pushed downward by the engaging pin 314 penetrating the long hole 321a, and the pivot arm The body 320 further rotates in the left rotation direction when viewed from the right side (see arrow M11). Thereby, the other end of the operation wire 145 connected to the second arm 322 is further pulled forward (see the arrow M12). Thus, as shown in FIG. 20C, the claw member 130 further rotates in the anti-engaging direction against the urging force of the spring 140 to reach the retracted position (see the arrow M13). That is, the claw member 130 at the disengaged position is further rotated in the anti-engagement direction from the disengaged position by the operation of the work clutch lever 23 so that the reaping clutch 75 is turned on. Rotate to the retracted position.

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

  In the combine 1 having the reverse rotation mechanism 110 according to the present embodiment, the controller 400 that controls 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 work clutch lever 23 is at the reverse rotation operation position P3. Thus, 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 when the reverse rotation switch 403 detects that the work clutch lever 23 is located at the reverse rotation operation position P3. An example of a configuration for performing such control will be described.

  As shown in FIG. 18, 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 that can be rotated by inserting a predetermined key into a keyhole, and is provided, for example, on a steering column located in front of the driver's seat 17 in the driver 15.

  Normally, when the starter switch 405 is turned on, current from the battery 406 flows into the coil of the starter relay connected to the starter, and the switch of the starter relay is turned on. As a result, the starter operates by energization from the battery 406, and the engine 25 starts. After the start of the engine 25, the driving state of the engine 25 and the supply of power from the battery 406 to each unit 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 work clutch lever 23 is at 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. Even when operated, the engine 25 is not started. That is, the controller 400 controls the current from the battery 406 not to flow into the coil portion of the starter relay so that the switch portion of the starter relay is maintained in the cut-off state (non-conducting state) in the state where the mowing reverse rotation is ON. Do. As a result, the power supply from the battery 406 to the starter is cut off, and the starter does not operate. 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 rotation switch 403, for example, an alarm buzzer is sounded, or the display unit such as a liquid crystal display device provided in the operation unit 15 displays, for example, " Turn off and start the engine. May be displayed. As a result, the middle position of the operator can be called out, and it is possible to accurately notify that the engine 25 cannot be started.

  According to the combine 1 of the present embodiment having the above-described configuration, in the configuration including the feeder 30 that transports and supplies the grain stalks cut by the cutting unit 3 to the threshing unit 7, the structure becomes complicated. With a simple structure, the conveyor 36 in the feeder 30 can be operated in the reverse rotation direction, and clogging of the grain in the feeder 30 can be eliminated.

  That is, in the combine 1 of the present embodiment, the harvesting input shaft 38 is engaged with the feeder house 35 by the reversing mechanism 110, so that the conveyor 36 is forcibly moved in the reverse direction using the raising operation of the feeder 30. It is provided with a configuration for rotating the motor. In other words, a configuration is provided in which the conveyor 36 is rotated in the reverse direction by power irrelevant to the transmission system that drives the working units such as the mowing unit 3 and the threshing unit 7.

  Thereby, in comparison with the conventional configuration in which the power transmission mechanism for reverse rotation of the conveyor is provided in the power transmission path from the engine to the reaping unit, the power transmission configuration from the engine 25 to the reaping unit 3 is not changed, and the conveyor is not changed. It is possible to realize a 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 raising operation of the feeder 30 by the lifting cylinder 39, the hydraulic pressure for operating the lifting cylinder 39 and the like in the combine 1 There is no particular need to change the device, nor is there any need to use extra power to operate the conveyor 36 in the reverse direction.

  Further, since the feeder 30 is raised by the action of the hydraulic pressure of the lifting / lowering cylinder 39, the lifting operation of the feeder 30 can easily obtain a larger operation force than the lowering operation of the feeder 30 due to its own weight. For this reason, even in a state where the feeder 30 is difficult to ascend and descend due to, for example, a clogging action of the grain culm in the feeder house 35, the feeder 30 can be reliably raised, and the reverse rotation operation of the conveyor 36 by the reverse rotation mechanism 110 is reliably obtained. It becomes possible. In addition, since the raising operation of the feeder 30 is actively performed by the operation of the lifting / lowering cylinder 39, it is easier to control the operation as compared with the lowering operation of the feeder 30 due to its own weight. Good operability can be obtained for the reverse rotation operation.

  Further, according to the reverse rotation mechanism 110 according to the present embodiment, the reverse rotation mechanism 110 can be configured irrespective of the power transmission path from the engine 25 to the mowing unit 3. For this reason, it is not necessary to provide a structure for avoiding mutual interference of the power transmission for forward and reverse rotation of the conveyor 36 in the power transmission path from the engine 25 to the mowing unit 3, so that the structure becomes complicated and the device configuration becomes complicated. It is possible to make a configuration for operating the conveyor 36 in the reverse direction without increasing the size.

  Further, the reverse rotation mechanism 110 according to the present embodiment is configured such that a gear 120 supported by the cutting input shaft 38 and a claw member 130 supported by the feeder house 35 and provided on the feeder 30 side are main components. I have. According to such a configuration, the reversing mechanism 110 can be realized with an extremely simple configuration, and can be easily provided for the existing configuration of the combine 1.

  In addition, the reverse rotation mechanism 110 according to the present embodiment uses the gear 120 and the claw member 130 to move the cutting input shaft 38 in the reverse rotation direction in the operation state of the reverse rotation mechanism 110 to move the feeder 30 up and down. Is configured as a ratchet mechanism. According to such a configuration, the feeder 30 can be relatively rotated with respect to the cutting input shaft 38 when the feeder 30 descends in the operation state of the reverse rotation mechanism 110. Therefore, when the clogging of the grain stem in the feeder 30 is removed, the feeder 30 is moved up and down to move the conveyor 36 in the reverse direction by the raising operation of the feeder 30 a plurality of times. Can be performed smoothly.

  The combiner 1 according to the present embodiment includes an amplifying mechanism 200 that amplifies the amount of rotation of the rotating gear 120 by transmitting the ascent operation of the feeder 30 via the claw member 130 and transmits the amplified amount to the cutting input shaft 38. Prepare. According to such a configuration, it is possible to obtain a sufficient amount of rotation in the reverse rotation direction of the cutting input shaft 38 for operating the conveyor 36 in the reverse direction while using the raising and lowering operation of the feeder 30. That is, since the operation stroke of the raising and lowering operation of the feeder 30 is limited, it may not be possible to obtain a sufficient rotation amount for the rotation of the cutting input shaft 38 in the reverse rotation direction to eliminate the clogging of the grain stalk. However, by providing the amplifying mechanism 200, the amount of rotation of the cutting input shaft 38 due to the rotation of the gear 120 due to the upward rotation of the feeder 30 can be amplified. This makes it possible to easily obtain a sufficient amount of operation for the operation of the conveyor 36 in the reverse direction, and to effectively eliminate clogging of the cereal stem.

  The amplifying mechanism 200 also includes an input shaft side gear (first gear 211 and fourth gear 214) supported by the cutting input shaft 38, an idler shaft 215, and meshed with the input shaft side gear supported by the idler shaft 215. And a transmission shaft side gear (a second gear 212 and a third gear 213). According to such a configuration, the amplification mechanism 200 can be simply configured using the existing configuration, and the effect of amplifying the amount of rotation 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 on the left and right sides of the machine body with respect to the feeder house 35. According to such a configuration, the disposition portion of the reversing mechanism 110 is the outer left side portion of the combine 1, so that accessibility to the reversing mechanism 110 can be improved. Thereby, good maintenance properties can be obtained for the reverse rotation mechanism 110. Therefore, for example, assuming a configuration in which the arrangement of the feeder 30 of the cabin 16 is left-right reversed with respect to the combine 1 according to the present embodiment, the reversing mechanism 110 moves the feeder house 35 to the right and left outer sides of the machine body. 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 driving unit 15. According to such a configuration, the operator during the driving operation in the driving unit 15 can operate the reversing mechanism 110 without leaving the driver's seat 17, so that it is preferable to remove the clogged grain culm. Operability can be obtained.

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

  Further, by adopting a configuration in which the reversing mechanism 110 is operated by the work clutch lever 23, the existing operating tool provided in the driving unit 15 can be shared as the operating tool of the reversing mechanism 110. It is necessary to separately provide an operation unit for operation, and the configuration of various operation units provided in the operation unit 15 can be simplified.

  Furthermore, for example, in the case of a configuration in which the reverse rotation mechanism 110 is operated by an operating tool provided separately from the work clutch lever 23, the cutting clutch 75 and the reverse rotation mechanism 110 are operated independently of each other. A configuration for avoiding the operation of the reverse rotation mechanism 110 in the ON state of 75 (both forward and reverse biting) is required. In this regard, by adopting a configuration in which the reverse rotation mechanism 110 is operated by the work clutch lever 23, it is possible to use a common operating tool for the reaping clutch 75 and the reverse rotation mechanism 110. By making the operation of the reverse rotation mechanism 110 different from the operation of the reverse rotation mechanism 110, the forward and reverse biting can be reliably avoided.

  Further, in the configuration in which the reverse rotation mechanism 110 can be operated by the work clutch lever 23, the work clutch lever 23 has the stop operation position P0 and the first work operation position P1 where the work clutch lever 23 has moved rightward from the stop operation position P0. And a reverse rotation operation position P3 moved backward from the stop operation position P0. According to such a configuration, it is possible to avoid suddenly moving the work clutch lever 23 to the reverse rotation operation position P3, and it is possible to obtain good workability.

  In particular, in the present embodiment, the work clutch lever 23 has, as its operation positions, a stop operation position P0, a first work operation position P1, a second work operation position P2, and a reverse rotation operation position P3. A crank-shaped operation movement path having a path end or a path corner is formed. According to such a configuration, the shape of the operation movement path of the work clutch lever 23 serves as a check means, and it is possible to prevent the reverse rotation mechanism 110 from being erroneously operated during the reaping work as much as possible. This makes it possible to prevent damage to the components such as the conveyor 36 and the reversing mechanism 110.

  Specifically, regarding the movement operation of the work clutch lever 23, the work clutch lever 23 is moved in a direction different from the movement direction (right direction in the present embodiment) for driving the work unit starting from the stop operation position P0 (rearward direction in the present embodiment). The moving operation is an operation for operating the reversing mechanism 110. For this reason, it is possible to prevent the reverse rotation mechanism 110 from being operated due to an unexpected movement of the work clutch lever 23 due to an erroneous operation or the like from a state where the work unit is operated by the operation position of the work clutch lever 23.

  That is, assuming that the movement operation of the work clutch lever 23 is such that the movement operation for driving the work unit and the movement operation for operating the reversing mechanism 110 are operations on the movement paths that are continuous with each other along a common straight line. In this case, for example, it is conceivable that the reverse rotation mechanism 110 is suddenly operated unintentionally due to an erroneous operation of the work clutch lever 23 or the like. Therefore, the lever guide section 150 of the work clutch lever 23 is provided as a movement path section for the reverse rotation mechanism 110 in a direction different from the first movement path section 161 via the stop operation position P0 in the neutral state. It has three moving route sections 163. Therefore, when the reverse rotation mechanism 110 is operated, the working unit can be reliably turned off, and unintended operation of the reverse rotation mechanism 110 can be avoided, so that high safety can be obtained.

  In the present embodiment, the operation direction of the work clutch lever 23 for operating the reverse rotation mechanism 110 is the rearward direction, and the operation direction of the work clutch lever 23 for turning on the reaping clutch 75 is the forward direction. It is in the opposite direction. According to such a configuration, the operation of the work clutch lever 23 for operating the reversing mechanism 110 which directly interferes with the operation of the reaper 3 is replaced with the work clutch lever 23 for operating the reaper 3. Operation can be clearly separated, and higher safety can be obtained.

  In the present embodiment, the claw member 130 is connected to the work clutch lever 23 by a link mechanism 300 including an operation wire 145, and is urged by a spring 140 in a direction to engage with the gear 120. A configuration is employed in which the claw member 130 is held in a disengaged state with the gear 120 by pulling the 130 against the spring 140 with the operation wire 145. According to such a configuration, when the engagement of the claw member 130 is released and the reverse rotation mechanism 110 is deactivated, the claw member 130 is pulled by the operation wire 145, so that the engagement of the claw member 130 is surely achieved. Can be canceled.

  That is, if a configuration in which the engagement of the claw member 130 is released by the urging force of the spring is adopted, the operation of the work clutch lever 23 is not sufficiently transmitted to the claw member 130 via the spring depending on the state of the spring or the like. Further, there is a possibility that the claw member 130 remains engaged with the gear 120 by the action of the spring. Therefore, by employing the pulling 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 work clutch lever 23 can reliably bring the reverse rotation mechanism 110 into the non-operation state. Further, the rotation of the claw member 130 in the engagement direction is performed by using the biasing force of the spring 140, so that the claw member 130 can be rotated as compared with, for example, a configuration using a wire separately from the operation wire 145 for disengaging. Can be realized with a simple configuration.

  In the present embodiment, the link mechanism 300 that connects the pawl member 130 and the work clutch lever 23 to each other disengages the pawl member 130 from the engaged 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 directions of the disengagement position and the retreat position in the mating direction. According to such a configuration, when the work clutch lever 23 is in the operation position where the operation of the mowing unit 3 that directly interferes with the operation of the reverse rotation mechanism 110 is turned on, the claw member 130 is engaged. Can be reliably evacuated. Accordingly, it is possible to reliably prevent the claw member 130 from engaging with the gear 120 while the mowing unit 3 is operating, and to obtain high safety.

  In addition, the combine 1 of the present embodiment includes the reverse rotation switch 403, and controls the start and stop of the engine 25 by the controller 400 based on the detection signal. According to such a configuration, it is possible to prevent the engine 25 from starting in a state in which the work clutch lever 23 is in the reverse rotation operation position P3 where the reverse rotation mechanism 110 is in the operating state (the state in which the harvest reverse rotation is ON). Thus, for example, by raising the feeder 30 after the start of the engine 25 in the cutting reverse rotation ON state, the cutting input shaft 38 rotates in the reverse rotation direction, and the rotation of the cutting input shaft 38 causes the cutting input shaft 38 to rotate. It is possible to solve the problem that the respective operating units of the cutting unit 3 such as the conveyor 36 and the cutting blade device 32 that operate by receiving the power transmitted from the unit 38 operate unintentionally. As a result, high security can be obtained.

  The combine according to the present invention described using the embodiments as described above is not limited to the above-described embodiments, and various modes can be adopted within the scope of the gist of the present invention.

  In the above-described embodiment, the elevating cylinder 39 for raising and lowering the feeder 30 is a single-acting hydraulic cylinder that applies a hydraulic pressure when raising the feeder 30. However, the present invention is not limited to this. It may be a reciprocating cylinder.

  In the above-described embodiment, the working clutch lever 23 for operating the reaping unit 3 and the threshing unit 7 is used as an operating tool for operating the reversing mechanism 110, but is not limited to this. Absent. The operating tool for operating the reversing mechanism 110 is an operating tool for operating either the cutting unit 3 or the threshing unit 7 or an operating tool separately provided for operating the reversing mechanism 110. Or you may. However, from the viewpoint of simplifying the configuration using the existing configuration and avoiding the simultaneous operation of the reversing mechanism 110 and the working unit such as the mowing unit 3, the operating tool of the reversing mechanism 110 is used. Is preferably a work operation tool for performing at least one of the operation of the cutting unit 3 and the threshing unit 7.

  In the above-described embodiment, the lever guide portion 150 of the work clutch lever 23 has a substantially crank shape as a whole due to the first movement route portion 161, the second movement route portion 162, and the third movement route portion 163. It is configured to do so, but is not limited to this. In the lever guide portion 150, the direction (second direction) along which the third movement path portion 163 extends 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. Any direction may be used as long as it is different from the direction along which the movement route section 161 (the first direction) follows. Therefore, for example, the third movement path section 163 is provided forward from the stop operation position P0, and the lever guide section 150 has a substantially "U" shape as a whole by each movement path section. Is also good.

  Further, in the above-described embodiment, the control for stopping the start of the engine 25 is performed as the start / stop control of the engine 25 by cutting off the power supply from the battery 406 to the starter by the controller 400, but is not limited thereto. Not something. Regarding the start / stop control of the engine 25, in a configuration in which the reverse rotation mechanism 110 is operated by the work clutch lever 23, the engine 25 is controlled based on the output signal of the reverse rotation switch 403 that detects that the work clutch lever 23 is at the reverse rotation operation position P3. The control configuration and control contents are not particularly limited as long as the control is to stop the start.

DESCRIPTION OF SYMBOLS 1 Combine 2 Traveling body 3 Cutting part 6 Body frame 7 Threshing part 23 Work clutch lever (work operation tool)
25 engine 30 feeder (transport device)
35 Feeder House (Housing)
36 Conveyor 38 Cutting input shaft (input shaft)
39 Cylinder for lifting and lowering 57 Threshing clutch 75 Cutting clutch 110 Reverse rotation mechanism 120 Gear (first engagement member)
130 Claw member (second engagement member)
140 spring (biasing member)
145 operation wire (wire member)
161 First moving path section 162 Second moving path section 163 Third moving path section 200 Amplifying mechanism 211 First gear (input shaft side gear)
212 2nd gear (transmission shaft side gear)
213 3rd gear (input shaft side gear)
214 4th gear (transmission shaft side gear)
215 Idler shaft (transmission shaft)
300 Link mechanism 403 Reverse switch 400 Controller (control unit)
P0 Stop operation position P1 First operation position P2 Second operation position P3 Reverse operation position

Claims (1)

A combine equipped with a transport device that transports the grain stalks that have been cut at the cutting unit and supplies the culms to the threshing unit,
The transfer device has, in a housing, a conveyor having a drive shaft as an input shaft that receives power transmission in the left-right direction as an axial direction, and moves up and down by rotating the combine device around the input shaft. It is provided so that
A reversing mechanism that transmits the ascending operation of the transport device to the input shaft, and rotates the input shaft in a direction opposite to the rotation direction at the time of transporting the cereal stem with the ascending operation of the transport device,
The combine is characterized in that the reversing mechanism is provided outside a rear end of the transport device in the left-right direction.

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