JP2014158454A - Combine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress the adhesion of dust to an outside air intake port accompanied by the take-in of cooling air without complicating a structure, in a normal-type combine.SOLUTION: A normal-type combine comprises: a traveling machine body 1 mounted with an engine 7 as a power source; a reaper 3 having a reaping blade 15; and a thresher 9 having a threshing cylinder 21. The engine 7 is arranged at one side of the rear of the thresher 9 in the traveling machine body 1, and an engine water cooling radiator 172, the engine 7, and a cooling fan 170 for air-cooling the radiator are arranged in front of the engine 7. A cooling air passage is formed of a cover duct body 173 which covers a region toward the front of the radiator 172 and the cooling fan 170 from the other side of a side opposite to the thresher 9 in the engine 7.

Description

  The present invention relates to a combine equipped with a reaping device for reaping uncut cereal grains in a field and a threshing apparatus for threshing grains of the harvested cereal grains.

  Conventionally, a traveling machine body having a traveling unit and a driver's seat, a reaping device having a cutting blade, a threshing device having a handling cylinder, a feeder house for supplying reaped cereals from the reaping device to the threshing device, and an engine for driving each unit And a grain sorting mechanism for sorting the threshing material of the threshing device, and a grain tank that collects the grain of the threshing device, and there is a technology for continuously harvesting and threshing the uncut cereal grains in the field (Patent Document) 1). In addition, a cooling fan and a radiator are arranged on the left and right sides of the engine mounted on the traveling machine body, a cover duct is further arranged on the left and right outside of the cooling fan and the radiator, and external air ( A technique for taking in cooling air and cooling the radiator is also well known (see Patent Document 2).

JP 2008-263865 A JP 2004-204827 A

  In the prior art shown in Patent Document 1, the cover duct is placed opposite to the engine supported by vibration isolation on the traveling machine body, so the outside air intake of the cover duct is placed at a height position relatively close to the farm field. Yes. Further, since the cover duct is disposed on the side facing the output shaft of the engine, the opening area of the outside air intake is relatively small. Due to these factors, the suction pressure of the cooling air tends to be high at the outside air inlet, and dust such as dust is attached to the outside air inlet as the cooling air is taken in, and if dust accumulates, the outside air intake The mouth was sometimes clogged.

  On the other hand, in Patent Document 2, a technology is adopted in which the direction of the wind is changed between the outside air intake direction and the outside air discharge direction by switching the direction of the cooling fan blades, the wind direction is set in the outside air discharge direction, and the outside air intake port is set. The attached dust is blown away and removed. However, when the technique of Patent Document 2 is adopted to prevent clogging, a structure for switching the direction of the blades of the cooling fan is provided, and an operation structure for switching the direction of the blades is also provided. There has been a problem that the cost of parts has increased and it has not met the demand for cost reduction that has been increasing in recent years. Since the cover duct is not configured to be openable and closable, not only the work area required for maintenance of the engine disposed in the engine room is reduced, but also maintenance in the duct is difficult.

  Therefore, the present invention seeks to provide a combine that has been improved by examining these current conditions.

  In order to achieve the above object, a combine of an invention according to claim 1 is a traveling machine body equipped with an engine as a power source, a mowing device having a cutting blade, a threshing device having a handling cylinder, and the engine water cooling. A radiator, a cooling fan for cooling the engine and the air for the radiator, the engine is installed on one side of the rear part of the threshing device, and the radiator for cooling the engine water and the cooling fan in front of the engine And a cover duct body that forms a cooling air passage for the engine by covering a region from the other side opposite to the threshing device to the front of the radiator and the cooling fan in the combine. And the side duct body constituting the side part of the cover duct body is configured to be openable and closable outside. That.

  The invention according to claim 2 is the combine according to claim 1, wherein the cover duct body communicates with the side duct body and an opening provided on the front left side of the side duct body. And a front duct body that covers the front of the engine, and the side duct body is hinged at the rear end side and can be opened and closed from the front side, and is configured to be detachable from the front duct body. It is.

  According to a third aspect of the present invention, in the combine according to the second aspect, the height position of the side duct body is set higher than the height position of the front duct body. An outside air inlet is formed on the outer side surface, and the lower side of the side duct body is formed in an opening exposing a lower portion on the other side of the engine, and the opening is covered with a removable side cover. Is.

  According to a fourth aspect of the present invention, there is provided the combine according to any one of the first to third aspects, wherein a pump case including a left and right hydraulic pump is installed on the right side of the engine in the left-right width direction of the traveling machine body. In addition, a left and right hydraulic motor whose braking is controlled by the left and right hydraulic pumps are installed on the left side of the engine, and a hydraulic pipe connecting the pump case and the left and right hydraulic motors is provided on the lower side of the cover duct body. It is piped so as to bypass the front side.

  According to invention of Claim 1, the traveling body which mounts the engine as a motive power source, the cutting device which has a cutting blade, the threshing apparatus which has a handling cylinder, the radiator for engine water cooling, the engine, and the radiator In the combine provided with a cooling fan for air cooling, the engine is installed on one side of the rear part of the threshing device, and the radiator for cooling the engine water and the cooling fan are arranged in front of the engine, The engine includes a cover duct body that forms a cooling air passage of the engine by covering a region from the other side opposite to the threshing device to the front of the radiator and the cooling fan. Since the side duct body constituting the side part of the engine is configured to be openable and closable outward, On the other side of the cover duct body to be, it is possible to form a wide outside-air inlet opening area. For this reason, it is possible to suppress the suction pressure while ensuring a sufficient amount of cooling air to be taken into the cooling air passage, and to reduce adhesion of dust and the like accompanying the intake of the cooling air. In addition, since the side duct body is configured to be openable and closable, not only maintenance inside the engine room can be easily performed, but also dust removal work inside the cover duct body can be removed. Ability can be maintained.

  According to a second aspect of the present invention, the cover duct body has an opening communicating with the side duct body and an opening provided on the front left side of the side duct body and covers the front of the engine. A front duct body, and the side duct body is configured to be detachable from the front duct body so that a rear end side thereof is hinged and can be opened and closed from the front side. By opening the side duct body, the work inside the ducts of the side duct body and the front duct body can be easily performed. Therefore, the intake capacity of the cover duct body can be maintained by removing dust and the like inside the duct.

  According to invention of Claim 3, the height position of the said side part duct body is set higher than the height position of the said front part duct body, and the external air intake is formed in the side surface of the said machine part outer side in the said side part duct body. The lower side of the side duct body is formed in an opening exposing a lower portion on the other side of the engine, and the opening is covered with a detachable side cover. As much as the height of the body moves away from the field, it is highly effective in preventing dust such as sawdust. Moreover, the lower side of the side duct body is formed in an opening in which the lower part on the other side of the engine is exposed, and the opening is covered with a detachable side cover. There is also an advantage that maintenance work such as cleaning and maintenance of the engine and the like can be easily performed by effectively utilizing the formed opening to expose the lower part of the other side of the engine by removing the side cover.

  According to the invention of claim 4, in the left-right width direction of the traveling machine body, a pump case having a left-right hydraulic pump is installed on the right side of the engine, and braking is controlled by the left-right hydraulic pump. Is installed on the left side of the engine, and the hydraulic pipe connecting the pump case and the left and right hydraulic motors is piped so as to bypass the front side of the engine under the cover duct body, By disposing the pump case in the same direction as the cover duct body, a complicated structure is not required for cooling the pump case, and maintenance work of the pump case can be facilitated. In addition, since the hydraulic piping bypasses the front side of the engine, it can be disposed overlapping with a complicated mechanism, and the increase in size of the machine can be prevented.

It is a left view of the combine which shows 1st Embodiment of this invention. It is a right view of the combine. It is a top view of the combine. It is a drive system figure of the combine. It is a rear view of the drive part of a combine. It is a front view of the drive part of a combine. It is the perspective view which looked at the cab from the front. It is a side view of a brake operation tool attachment part. It is the perspective view which looked at the attaching part of the brake operation tool from the front. It is the perspective view which looked at the attachment part of the brake operation tool from back. It is a hydraulic circuit diagram of a combine. It is sectional drawing of a mission case. It is the perspective view which looked at the mission case from back. It is a side view of a hydraulic motor attachment part. It is a top view which shows the structure of a cover duct body and an engine room frame. It is a top view which shows the internal structure of a cover duct body. It is a partially cutaway left view which shows the communication structure of a side part duct and a front part duct. It is front sectional drawing which shows the communication structure of a side part duct and a front part duct.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings (FIGS. 1 to 3) applied to a normal combine. 1 is a left side view of the combine, FIG. 2 is a right side view thereof, and FIG. 3 is a plan view thereof. First, the general structure of the combine will be described with reference to FIGS. In the following description, the left side in the forward direction of the traveling machine body 1 is simply referred to as the left side, and the right side in the forward direction is also simply referred to as the right side.

  As shown in FIGS. 1 to 3, the ordinary combine in the embodiment includes a traveling machine body 1 supported by a pair of left and right crawler belts 2 made of rubber crawlers as a traveling portion. At the front part of the traveling machine body 1, a reaping device 3 for capturing uncut cereal grains such as rice (or wheat, soybeans or corn) is mounted by a single-acting lifting hydraulic cylinder 4 so as to be adjustable up and down. ing. In addition, in the example of FIGS. 1-3, although the left-right paired crawler belt 2 used as a traveling part shall be comprised by the rubber crawler, it can also comprise also by iron crawler.

  A driver's cab 5 on which an operator is boarded is mounted on the front of the traveling machine body 1. A Glen tank 6 for storing the grain after threshing is disposed behind the cab 5. An engine 7 as a power source is disposed behind the Glen tank 6. On the right side of the rear part of the Glen tank 6, a grain discharge auger 8 is provided so as to be able to turn. The grain in the Glen tank 6 is configured so as to be carried out, for example, to a truck bed, a container, or the like from the throat throw opening 8a at the tip of the discharge auger 8. On the other side (left side in the embodiment) of the traveling machine body 1 is mounted a threshing device 9 for threshing the harvested cereal meal supplied from the harvesting device 3. In the lower part of the threshing device 9, a grain sorting mechanism 10 for performing swing sorting and wind sorting is arranged.

  The reaping device 3 includes a feeder house 11 that communicates with the front opening of the threshing device 9 and a horizontally long bucket-like grain header 12 that is connected to the front end of the feeder house 11. A scraping auger 13 is rotatably supported in the grain header 12. A take-up reel 14 with a tine bar is disposed above the front portion of the take-up auger 13. A clipper-shaped cutting blade 15 is disposed in front of the grain header 12. Left and right weed bodies 16 are provided to project from the left and right sides of the front part of the grain header 12. In addition, a feeder conveyor 17 is provided in the feeder house 11. Between the feed end of the supply conveyor 17 and the handling opening 9a, a beater cereal throwing beater 18 is provided. In addition, the lower surface part of the feeder house 11 and the front end part of the traveling machine body 1 are connected via the lifting hydraulic cylinder 4, and the reaping device 3 moves up and down by the lifting hydraulic cylinder 4.

  With the above configuration, the tip side of the uncut grain culm between the left and right weed bodies 16 is scraped by the scraping reel 14, and the heel side of the uncut grain culm is cut by the cutting blade 15, and the rotation of the scraping auger 13. By driving, the grain headers 12 are collected in the vicinity of the center of the left and right width. The whole amount of the harvested cereal meal of the grain header 12 is conveyed by the supply conveyor 17 and is configured to be put into the handling port 9a of the threshing device 9 by the beater 18. The grain header 12 is provided with a horizontal control hydraulic cylinder 19 for rotating the grain header 12 around the horizontal control fulcrum shaft 19a, and the grain header 12, The cutting blade 15 and the take-up reel 14 are supported horizontally with respect to the field scene.

  Moreover, as shown in FIGS. 1-3, the handling cylinder 21 is rotatably provided in the handling chamber of the threshing apparatus 9. As shown in FIG. A handling cylinder 21 is pivotally supported on a handling cylinder shaft 20 extended in the front-rear direction of the traveling machine body 1. On the lower side of the handling cylinder 21, a receiving net 24 for allowing the grains to leak is stretched. In addition, a spiral screw blade-shaped intake blade 25 projects outward in the radial direction on the outer peripheral surface of the front portion of the handling cylinder 21.

  With the above configuration, the harvested cereal mash introduced from the handling port 9 a is kneaded between the handling cylinder 21 and the receiving net 24 while being conveyed toward the rear of the traveling machine body 1 by the rotation of the handling cylinder 21 and threshing. Is done. The threshing of grains or the like smaller than the mesh of the receiving net 24 leaks from the receiving net 24. The sawdust and the like that do not leak from the receiving net 24 are discharged from the dust outlet at the rear of the threshing device 9 to the field by the conveying action of the handling cylinder 21.

  A plurality of dust feed valves (not shown) for adjusting the conveying speed of shed grains in the handling chamber are pivotally mounted on the upper side of the handling cylinder 21 so as to be rotatable. By adjusting the angle of the dust feed valve, the conveying speed (residence time) of threshing in the handling chamber can be adjusted according to the variety and properties of the harvested cereal. On the other hand, the grain sorting mechanism 10 disposed below the threshing device 9 includes a rocking sorter 26 for specific gravity sorting having a grain pan, a chaff sheave, a grain sheave, a Strollac, and the like.

  In addition, the grain sorting mechanism 10 includes a tang fan 29 that supplies sorting wind. The threshing that has been threshed by the handling cylinder 21 and leaked from the receiving net 24 is the first thing (grains) such as cereal grains by the specific gravity sorting action of the swing sorter 26 and the wind sorting action of the Kara fan 29. In addition, it is configured to be sorted into dust (such as re-sorted items) such as grain with branches and leaflets, and sawdust.

  A first conveyor mechanism 30 and a second conveyor mechanism 31 are provided on the lower side of the swing sorter 26 as the grain sorting mechanism 10. By selecting the swing sorter 26 and the tang fan 29, the first item such as the grain dropped from the swing sorter 26 is collected in the glen tank 6 by the first conveyor mechanism 30 and the cereal conveyor 32. A second thing such as a grain with a branch is returned to the sorting start end side of the swing sorting board 26 via the second conveyor mechanism 31 and the second reduction conveyor 33 and is re-sorted by the swing sorting board 26. . The sawdust and the like are configured to be discharged from the dust outlet 34 at the rear of the traveling machine body 1 to the field.

  Further, as shown in FIGS. 1 to 3 and 7, the cab 5 is provided with a control column 41 and a driver seat 42 on which an operator sits. The control column 41 (front column 41a, side column 41b) is tilted in the front-rear direction with left and right speed change levers 43 and 44 as control levers for changing the course of the traveling machine body 1 and changing the moving speed. A harvesting posture lever 45 for raising and lowering the harvesting reel 14 by raising and lowering the harvesting device 3 or tilting in the left-right direction, an accelerator lever 46 for controlling the rotation of the engine 7, and a grain for operating the grain discharge auger 8 A discharge lever 47 is arranged. A cutting clutch lever 39 for turning on and off the power transmission to the reaping device 3 and a threshing clutch lever 40 for turning on and off the power transmission to the threshing device 9 are also arranged. In addition, a guard frame 5a that an operator who sits on the driver's seat 42 grasps when standing is extended so as to surround the upper side and the left and right sides of the front column 41a. Further, a roof 49 for awning is attached to the upper side of the cab 5 via a support column 48.

  As shown in FIG. 1, left and right track frames 50 are arranged on the lower surface side of the traveling machine body 1. The track frame 50 includes a drive sprocket 51 that transmits the power of the engine 7 to the crawler belt 2, a tension roller 52 that maintains the tension of the crawler belt 2, a plurality of track rollers 53 that hold the ground side of the crawler belt 2 in a grounded state, An intermediate roller 54 that holds the non-grounding side of the crawler belt 2 is provided. The rear side of the crawler belt 2 is supported by the drive sprocket 51, the front side of the crawler belt 2 is supported by the tension roller 52, the grounding side of the crawler belt 2 is supported by the track roller 53, and the non-grounded side of the crawler belt 2 is supported by the intermediate roller 54 To be configured.

  Moreover, as shown in FIGS. 1-3, the bottom feed conveyor 60 arrange | positioned at the bottom part of the Glen tank 6 and the vertical feed conveyor 61 arrange | positioned at the rear part of the Glen tank 6 are provided. The left and right bottom feed conveyors 60 extend in the front-rear direction at the bottom of the grain tank 6 and convey the grains at the bottom of the grain tank 6 toward the lower end side of the vertical feed conveyor 61 provided vertically. The vertical feed conveyor 61 is extended in the vertical direction at the rear part of the grain tank 6, and conveys the grain from the upper end side of the vertical feed conveyor 61 toward the feed start end side of the grain discharge auger 8 on the right side of the grain tank 6. The grain in the Glen tank 6 is configured to be conveyed to the throat throwing port 8a at the leading end (feeding end side) of the discharge auger 8.

  The grain discharge auger 8 is supported on the upper end side of the vertical feed conveyor 61 so as to be rotatable in the vertical direction. The side of the grain discharge auger 8 that is the feed terminal side is configured to be movable up and down. In addition, it is configured such that the side of the spear throwing hole 8a can be moved around the conveyor axis of the vertical feed conveyor 61 (horizontal direction). That is, the hull throwing opening 8a side is moved to the front lower side of the traveling machine body 1, and the grain discharge auger 8 is stored in the right side of the cab 5 and the Glen tank 6 via the auger rest 8b. On the other hand, the side of the grain discharge auger 8, which is the feed terminal side, is raised, the side of the traveling machine body 1 is moved to the side or rear of the traveling machine body 1, and the side of the traveling machine body 1 is moved to the side or rear of the traveling machine body 1. The grain discharge auger 8 is made to project, the pallet throwing port 8a is made to face the truck bed or container, and the grain in the glen tank 6 is carried out to the truck bed or container.

  Next, the drive structure of the combine will be described with reference to FIGS. 4 to 6 and FIG. As shown in FIGS. 4 and 11, a pump case 66 for traveling speed change having a pair of swash plate variable left and right traveling hydraulic pumps 65 is provided. The engine 7 is mounted on the upper surface of the right rear portion of the traveling machine body 1, and the pump case 66 is disposed on the upper surface of the traveling machine body 1 on the right side of the engine 7. Also, left and right reduction gear cases 63 are provided at the rear ends of the left and right track frames 50, respectively. A traveling hydraulic motor 69 is disposed in each of the left and right reduction gear cases 63. A travel drive input shaft 64 projecting rearward from the pump case 66 and an output shaft 67 projecting rearward from the engine 7 are connected via a travel output belt 230. The engine 7 and the pump case 66 are provided on the upper surface side of the traveling machine body 1 on the rear side of the threshing device 9, and the engine 7 is disposed between the threshing device 9 and the pump case 66.

  A charge pump 68 that drives the lifting hydraulic cylinder 4 and the like of the reaping device 3 is also provided on the same axis 64 as the traveling hydraulic pump 65. Further, the working hydraulic pump 70 for operating the lifting hydraulic cylinder 4 of the reaping device 3 or the horizontal control hydraulic cylinder 19 of the reaping device 3 is provided, the working hydraulic pump 70 is disposed in the engine 7, and the traveling hydraulic pump 65 is provided. In the same manner, the charge pump 68 and the working hydraulic pump 70 are driven by the engine 7.

  With the above configuration, the drive output of the engine 7 is transmitted to the left and right traveling hydraulic pump 65 via the output shaft 67. The left and right traveling hydraulic motors 69 are individually driven by the left and right traveling hydraulic pumps 65, and the left and right crawler belts 2 are moved forward and backward by the left and right traveling hydraulic motors 69. Further, the rotational speed of the left and right traveling hydraulic motor 69 is controlled, and the rotational speed of the left and right crawler belts 2 driven by the left and right traveling hydraulic motor 69 is varied to change the moving direction (traveling path) of the traveling machine body 1 and It is configured to perform direction changes on the ground.

  That is, as shown in FIG. 11, a pair of left and right traveling hydraulic motors 69 are hydraulically connected to the left and right traveling hydraulic pumps 65 via a closed loop hydraulic circuit 261. The left and right crawler belts 2 are driven in the forward direction or the reverse direction via the drive sprocket 51 by the left and right traveling hydraulic motor 69. The operator operates the left and right shift levers 43 and 44 to adjust the angle of the output adjustment swash plate 65a (shift control) of the left and right traveling hydraulic pumps 65, respectively. The rotation direction is changed, and the left and right crawler belts 2 are driven independently of each other, so that the traveling machine body 1 moves forward or backward.

  As shown in FIGS. 4 to 6, an engine room 57 is formed by the engine room frame 56, and the engine 7 is installed in the engine room 57. A threshing input first counter shaft 71 is pivotally supported on the engine room frame 56 via a first bearing body 58. Further, a second countershaft 72 for threshing input is pivotally supported on the engine room frame 56 via the second bearing body 59. The first counter shaft 71 is connected to the output shaft 67 of the engine 7 via the work output belt 231. A second countershaft 72 is connected to the first countershaft 71 via a threshing drive belt 232. The power of the engine 7 is transmitted from the first counter shaft 71 to the second counter shaft 72 via the threshing clutch 233 also serving as a tension roller and the threshing drive belt 232. The threshing clutch 233 is controlled to be turned on and off by the operator's lever operation. Further, a second counter shaft 72 is connected to one end side (rear end side) of the barrel shaft 20 via a barrel driving belt 234. By the turning-on / off operation of the threshing clutch 233, the handling cylinder 21 is driven and controlled via the second counter shaft 72, and the cereal mash introduced from the beater 18 is continuously threshed by the handling cylinder 21. .

  Further, a cutting selection input case 73 is provided on the front wall of the threshing device 9. A cutting selection input shaft 74 is pivotally supported on the cutting selection input case 73. One end side (right end portion) of the cutting selection input shaft 74 is connected to the other end side (front end side) of the barrel 20 via a bevel gear 75. The other end side (left end portion) of the cutting selection input shaft 74 is connected to the left end portion of the beater shaft 82 on which the beater 18 is pivotally supported via the beater drive belt 238. The left end portion of the beater shaft 82 is connected to the left end portion of the hot shaft 76 supporting the hot fan 29 via a selection input belt 235. A tang shaft 76 is connected to the left end of the first conveyor shaft 77 of the first conveyor mechanism 30 and the left end of the second conveyor shaft 78 of the second conveyor mechanism 31 via a conveyor drive belt 237. . A left end portion of a second conveyor shaft 78 is connected to a left end portion of a crank-like swing drive shaft 79 pivotally supported by the rear portion of the swing sorting plate 26 via a swing sorting belt 236. The cereal conveyor 32 is driven via the first conveyor shaft 77, and the first selected grain of the first conveyor mechanism 30 is collected in the glen tank 6. In addition, the second reduction conveyor 33 is driven via the second conveyor shaft 78, and the second selected grain mixed with the sawdust from the second conveyor mechanism 31 is returned to the upper surface side of the rocking sorter 26.

  On the other hand, the left end portion of the cutting input shaft 89 on which the feed end side of the supply conveyor 17 is pivotally connected is connected to the left end portion of the beater shaft 82 via a cutting drive belt 241 and a cutting clutch 242. The right end of the cutting input shaft 89 is connected to the header drive shaft 91 provided on the grain header 12 via the header drive chain 90. A header drive shaft 91 is connected to a drive shaft 93 that supports the drive auger 13 via a drive drive chain 92. A header drive shaft 91 is connected to a reel shaft 94 that supports the take-up reel 14 via an intermediate shaft 95 and reel drive chains 96 and 97. Further, the cutting blade 15 is connected to the right end portion of the header driving shaft 91 via a cutting blade driving crank mechanism 98. By the turning-on / off operation of the mowing clutch 242, the feed conveyor 17, the auger 13, the hoisting reel 14, and the cutting blade 15 are driven and controlled so as to continuously mow the tip of the uncut grain culm in the field. It is configured.

  Further, as shown in FIG. 4, the rear end portion of the lower intermediate shaft 105 is connected to the rear end portion of the first counter shaft 71 via the grain discharge belt 244 and the grain discharge clutch 245. The rear end side of the lower intermediate shaft 105 is connected to the rear end portion of the bottom feed conveyor shaft 103 via a longitudinal feed drive chain 104. The front end side of the intermediate shaft 105 is connected to the lower end side of the vertical feed conveyor shaft 106 of the vertical feed conveyor 61 via a bevel gear mechanism 107. One end side of the upper intermediate shaft 109 is connected to the upper end side of the vertical feed conveyor shaft 106 via a bevel gear mechanism 108. One end side of the grain discharge shaft 111 is connected to the other end side of the upper mediation shaft 109 via the grain discharge drive chain 110. The feed start end side of the discharge auger shaft 112 of the grain discharge auger 8 is connected to the other end side of the grain discharge shaft 111 via a bevel gear mechanism 113. The bottom feed conveyor 60, the vertical feed conveyor 61, and the grain discharge auger 8 are driven and controlled by the turning-on / off operation of the grain discharge clutch 245 so that the grains in the glen tank 6 are discharged to a truck bed or a container. It is composed.

  Further, as shown in FIG. 2, front and rear grain discharge ports 221 and 222 are provided at the bottom of the Glen tank 6. Moreover, the wrinkle receiving base 223 is arrange | positioned so that insertion / extraction is possible in the traveling machine body 1 upper surface side below the grain discharge ports 221,222. An operator other than the operator of the driver's seat 42 gets on the heel support 223 with the heel support 223 supported in a horizontal working posture, and attaches a heel bag (not shown) to the heel support bar 224. The grain in the Glen tank 6 is discharged into the bag. The straw bag filled with the grain is dropped from the straw tray 223 to the field and collected.

  With the above configuration, the grains in the grain tank 6 can be discharged without interrupting the mowing and threshing operation by discharging the grains in the grain tank 6 from the grain discharge ports 221 and 222. That is, compared with the work of discharging the grain in the grain tank 6 from the grain discharge auger 8, there is almost no need to interrupt the mowing and threshing work. Work efficiency can be improved.

  Further, as shown in FIGS. 2, 16, and 17, a shielding plate 225 is connected to the traveling machine body 1 and the bottom of the Glen tank 6 at a portion where the grain outlets 221 and 222 are provided. The upper portion of the shielding plate 225 is connected to the bottom portion of the Glen tank 6 by bolt fastening or the like, and the lower portion thereof is connected to the traveling machine body 1. That is, the shielding plate 24 is installed between the intake side of the tang fan 29 and the mounting position of the straw bag below the grain outlets 221 and 222. Therefore, the mounting position of the bag is shielded from the intake side of the tang fan 29 by the shielding plate 24. It is possible to prevent the straw bag attached to the straw catcher 224 from being sucked into the grain sorting mechanism 10 by the rotation of the Kara fan 29.

  Next, the hydraulic structure of the combine will be described with reference to FIG. As shown in FIG. 11, as the hydraulic actuator, the harvesting lifting hydraulic cylinder 4, the horizontal control hydraulic cylinder 19, the left and right reel lifting hydraulic cylinders 251 that support the take-up reel 14 so as to be lifted and lowered, and the grain An auger lifting / lowering hydraulic cylinder 252 that supports the discharge auger 8 to be movable up and down is provided. The working hydraulic pump 70 is hydraulically connected to the horizontal control hydraulic cylinder 19 through the horizontal control electromagnetic hydraulic valve 253 that is controlled by the operation of the horizontal control switch 254 in the gripping posture lever 45 grip. Based on the operator's operation of the horizontal control switch 254 or the detection result of the left / right tilt sensor (not shown), the horizontal control hydraulic cylinder 19 is activated to maintain the horizontal tilt angle of the traveling machine body 1 at a horizontal or arbitrary tilt angle. To do.

  Further, the working hydraulic pump 70 is hydraulically connected to the cutting lift hydraulic cylinder 4 via the cutting lift manual hydraulic valve 255. By the operation of tilting the cutting posture lever 45 in the front-rear direction, the cutting lifting / lowering hydraulic cylinder 4 is actuated so that the operator moves the cutting device 3 up and down to an arbitrary height (for example, cutting height or non-working height). It is configured. On the other hand, the working hydraulic pump 70 is hydraulically connected to the reel lifting hydraulic cylinder 251 through the reel lifting manual hydraulic valve 256. The operation of tilting the harvesting posture lever 45 in the left-right direction actuates the reel lifting hydraulic cylinder 251 and the operator moves the take-up reel 14 up and down to an arbitrary height so as to harvest uncut grain culm on the field. doing.

  On the other hand, the working hydraulic pump 70 is hydraulically connected to the auger lifting hydraulic cylinder 252 via the auger lifting manual hydraulic valve 257. By a tilting operation of the grain discharge lever 47 in the front-rear direction, the auger lifting / lowering hydraulic cylinder 252 is operated, and the operator moves the cocoon throwing port 8a of the grain discharging auger 8 up and down to an arbitrary height. In addition, the grain discharge auger 8 is rotated in the horizontal direction by an electric motor (not shown), and the cocoon throwing port 8a is moved in the horizontal direction. In other words, the hull throwing port 8a is positioned above the truck bed or container, and the grains in the grain tank 6 are discharged into the truck bed or container.

  Further, as shown in FIG. 11, left and right traveling hydraulic motors 69 are hydraulically connected to the left and right traveling hydraulic pumps 65 via left and right closed loop hydraulic circuits 261, respectively. The left and right speed change levers 43 and 44 are connected to the output adjusting swash plate 65a of the left and right traveling hydraulic pumps 65 via a servo valve mechanism 262, respectively, and are proportional to the front and rear tilt angles of the left and right speed change levers 43 and 44. Thus, the support angle of the output adjusting swash plate 65a is changed. That is, the left and right traveling hydraulic motors 69 are respectively driven by the left and right traveling hydraulic pumps 65, and the driving force of the left and right traveling hydraulic motors 69 is transmitted to the left and right crawler belts 2 via the reduction gear mechanism 263 of the reduction gear case 63, respectively. The left and right crawler belts 2 are driven forward or backward.

  With the above configuration, by tilting the left and right shift levers 43 and 44 forward, the vehicle can move straight forward in the forward direction at a vehicle speed proportional to the tilt angle of the left and right shift levers 43 and 44. By tilting the left and right speed change levers 43 and 44 toward the rear of the machine body, the left and right speed change levers 43 and 44 can be moved straight in the backward (reverse) direction at a vehicle speed proportional to the tilt angle of the left and right speed change levers 43 and 44. On the other hand, when the left and right speed change levers 43 and 44 have different inclination angles to the front of the body, or when the left and right speed change levers 43 and 44 have different inclination angles to the rear of the body, When one of the 44 is tilted forward of the aircraft and the other is tilted backward of the aircraft, the course of the traveling aircraft 1 can be corrected in the left-right direction.

  In other words, when the operation amount or the operation direction of the left and right speed change levers 43 and 44 are made different, the difference in the tilt angle of the left and right speed change levers 43 and 44 at a vehicle speed proportional to the tilt angle of the left and right speed change levers 43 and 44. The traveling machine body 1 can be swung in the left-right direction with a turning radius proportional to. The left and right closed loop hydraulic circuits 261 are connected to the high pressure oil discharge side of the charge pump 68 via the oil cooler 264 and the line filter 265 so that the hydraulic oil in the oil tank 266 is supplied to the left and right closed loop hydraulic circuits 261. It is configured. Further, as shown in FIGS. 11 and 12, a brake mechanism 297 having a brake brake lever 296 is provided on the motor shaft 295 of the traveling hydraulic motor 69. A brake mechanism 297 is actuated by operating a brake brake lever 296 to brake the motor shaft 295.

  Next, with reference to FIGS. 7 to 10, a mounting structure of the brake pedal 38 as the brake operating tool and the traveling speed change levers 43 and 44 will be described. As shown in FIGS. 8 to 10, a pedal frame 275 is erected from the cab 5, and a brake pedal 38 base end portion is pivotally supported on the pedal frame 275 via a pedal fulcrum shaft 276. One end side of the brake wire 278 is connected to the base end portion of the brake pedal 38 via the wire arm 277. Further, a pedal return spring 280 is connected to the base end portion of the brake pedal 38 via a spring arm 279. The pedal return spring 280 is configured to support the stepping portion 38a of the brake pedal 38 at the raised position. On the step floor 5 b of the driver's cab 5, a stepping portion 38 a is projected.

  As shown in FIGS. 8 to 10, the side column frame 281 forming the side column 41b includes an upper frame 281a that extends horizontally in the front-rear direction, a front column 281b that supports the front end of the upper frame 281a, It has an auxiliary column 281c erected in parallel with the front side of the column 281b, and an auxiliary upper frame 281d that connects the upper end of the column 281c to the front column 281b. The brake pedal 38 comes into contact with the lower surface of the auxiliary upper frame 281d, and the brake pedal 38 is supported at the raised position by the pedal return spring 280. Further, the parking lever 283 is rotatably supported by the auxiliary column 281c and the auxiliary upper frame 281d via the upper and lower brackets 282. When the brake pedal 38 is moved down by a stepping operation against the pedal return spring 280, the pedal hook body 283a of the parking lever 283 is locked to the brake pedal 38, and the brake pedal is resisted against the pedal return spring 280. 38 is configured to be supported in a downward movement (braking) position. A release spring 284 that supports the parking lever 283 is provided at a position where the pedal hook body 283a is not locked to the brake pedal 38.

  On the other hand, as shown in FIGS. 6 and 12 to 14, the brake wire 278 is suspended at the upper part of the traveling hydraulic motor 69 by a wire support frame 58 provided in the engine room frame 56 on the rear right side of the engine room 57. Yes. That is, the wire support frame 58 protrudes from the engine room frame 56 on the threshing device 9 on the front right side (engine 7 side), and further, a wire support plate 59 having a notch at the tip is provided at the tip of the wire support frame 58. Provided. On the other hand, a fixing member 278 b is provided at the end of the wire cover 278 a that covers the brake wire 278. And the nut which comprises the fixing member 278b pinches | interposes the wire support plate 59, and the other end side of the brake wire 278 is supported by the traveling body 1 upper side.

  The other end of the brake wire 278 supported on the upper side of the traveling machine body 1 is connected to the brake link body 286 via a brake spring 285. The brake link body 286 includes a rod-like driven body 286 a having an upper end connected to the brake spring 285 and a lower other end connected to the return spring body 293, and the driven body 286 a is connected to the upper and lower sides of the brake wire 278. Move up and down to match the movement. Further, the brake link body 286 has a link portion 286b connected to the left and right brake lever 296 via the link wire 298 in the front-rear direction with the driven body 286a as the center.

  By being configured in this manner, the brake link body 286 is connected to the return spring body 293 whose lower end is fixed by the traveling machine body 1 and the driven body 286a, so that the moving direction thereof is in the vertical direction. Be regulated. Therefore, the brake link body 286 moves up and down in accordance with the operation of the brake wire 278 connected via the brake spring 285. Further, the link portion 286b of the brake link body 286 is connected to the link wire 298 stretched on each of the left and right brake levers 296 at the same height position in the front-rear direction around the driven body 286a.

  At this time, the connection relationship of the link portion 286b, the left and right brake lever 296, and the left and right link wire 298 is symmetrical in the front-rear direction with the vertical movement direction of the driven body 286a as the center. That is, in the brake link body 286, the driven body 286a is disposed at a position that is the same distance as the connection position with the left and right link wires 298 having the same length along the front-rear direction of the traveling machine body 1. As a result, the brake link body 286 functions as a stabilizer body for operating the brake mechanism 297 that pulls the left and right brake levers 296 evenly. In this example, the brake link body 286 is configured such that the plate-like link portion 286b is separated from the driven body 286a, and the driven body 286a is sandwiched between the link body 286b. Another configuration may be employed, for example, the link portion 286b may be configured integrally.

  One end of each of the left and right link wires 298 is pivotally supported by a connecting shaft body 287 at a connecting portion with the link portion 286b, and is supported by a connecting shaft body 288 at a connecting portion with each of the left and right brake levers 296. The As shown in FIG. 6, the brake link body 286 moves up and down at a position where the link portion 286 b is directly above the left brake lever 296 in the lateral width direction of the traveling machine body 1. Accordingly, as shown in FIG. 13, the left link wire 298 is directly connected to the left brake lever 296, while the right link wire 298 is connected to the right brake lever 296 via the spacer 299.

  In this example, the brake link body 286 is positioned immediately above the left brake lever 296, but the present invention is not limited to this. For example, the brake link body 286 may be directly above the position that is in the middle of the left and right brake levers 29 as long as it can be arranged in the space on the traveling machine body 1. At this time, the left brake lever 296 is connected to the left link wire 298 via a spacer installed on the right side thereof, while the right brake lever 296 is connected to the right link wire 298 via a spacer installed on the left side thereof. Connecting.

  As described above, the brake wire 278 is connected to the left and right brake levers 296 by the brake link body 286 having a symmetrical shape with respect to the front-rear direction and the left and right link wires 298 having the same length. Therefore, the left and right brake levers 296 are evenly pulled by the brake link body 286 and the left and right link wires 298. Accordingly, the left and right link wires 298 are rotated by the same angle in accordance with the operation of the brake wire 278 to positions that are symmetrical in the front-rear direction.

  Further, as described above, since the left and right brake levers 296 are arranged symmetrically in the front-rear direction by the brake link body 286, the left and right traveling hydraulic motor 69 and the left and right reduction gear case 63 provided with the brake mechanism 297 are configured by the same parts. it can. That is, the left and right speed reduction gear case 63 and the left and right traveling hydraulic motor 69 are provided by arranging the components shown in FIG. 12 so as to be symmetrical about the vertical direction of the traveling machine body 1 (the moving direction of the brake link body 286). Is done.

  That is, the reduction gear case 63, the traveling hydraulic motor 69, the brake lever 296, and the link wire 298, which are configured as a braking mechanism for the left and right crawler belts 2, can be configured with the same components. Therefore, it is not necessary to make the braking mechanisms of the left and right crawler belts 2 separate components, and the configuration can be simplified, so that the assembly process can be simplified and the production efficiency can be increased. Further, with this configuration, the braking performance of the left and right crawler belts 2 can be functionally arranged, but the braking performance can be improved.

  Thus, the left and right brake lever 296 for braking the left and right brake mechanism 297 respectively, and the brake link body 286 as a brake operation stabilizer body connected to the brake pedal 38 as the brake operation tool via the brake wire 278, The link wire 298 connected to the brake link body 286 is configured so that the left and right brake levers 296 can be pulled evenly. Therefore, the left and right crawler belts 2 can be evenly braked, the malfunction of the left and right crawler belts 2 can be reduced, and the braking force of the left and right brake mechanism 297 can be properly maintained even in an inclined place.

  Furthermore, a positioning stopper body may be provided to support the left and right brake lever 296 at the brake release position. At this time, for example, the left and right positioning stopper bodies may support the left and right brake levers 296 in contact with each other and support them at the brake release position. Further, the left and right brake levers 296 may be supported at the brake release position by the positioning stopper body coming into contact with the brake link body 286 and restricting the downward movement of the brake link body 286. As a result, when the brake pedal 38 is stepped on, the left and right brake mechanisms 297 provided on the left and right traveling hydraulic motors 69 operate in a braking state. On the other hand, the brake mechanism 297 is released from the braking state by the return spring body 293 in a state where the stepping portion 38a of the brake pedal 38 is supported at the raised position.

  Next, as shown in FIGS. 8 to 10, a shift lever fulcrum that pivotally supports the left and right travel shift levers 43 and 44 so as to be pivotable in the front-rear direction on the upper frame 281 a of the side column frame 281 forming the side column 41 b. A shaft 411 is provided. The shift lever fulcrum shaft 411 is passed through the upper frame 281a, and the middle portion of the shift lever fulcrum shaft 411 is fixed to the upper frame 281a. The base end portions of the left and right traveling shift levers 43 and 44 and the middle portions of the left and right lever operation plates 412 and 413 are rotated to the left and right ends of the shift lever fulcrum shaft 411 protruding in the left-right direction from the upper frame 281a. Support it as possible. The left shift lever 43 and the left lever operation plate 412 are fixed together. The right travel shift lever 44 and the right lever operation plate 413 are integrally fixed. The left shift lever 43 (left lever operation plate 412) and the right shift lever 44 (right lever operation plate 413) are supported by the shift lever fulcrum shaft 411 so as to rotate independently. Yes.

  Further, by providing an interlocking detent ball mechanism 414 that releasably connects the left and right lever operation plates 412 and 413, the upper end sides of the left and right lever operation plates 412 and 413 are engaged by the interlocking detent ball mechanism 414, When either one of the left and right traveling speed change levers 43 and 44 is operated, the other is operated in conjunction with an operation load equal to or less than the engaging force of the interlocking detent ball mechanism 414. When the operation load is greater than the engaging force of the interlocking detent ball mechanism 414, only one traveling speed change lever 43 or 44 on the side where the operation is performed is operated.

  Furthermore, one end sides of the left and right shift push-pull wires 415 and 416 are coupled to the lower end sides of the left and right lever operation plates 412 and 413 via the left and right wire coupling shafts 419a and 419b, respectively. The other end sides of the left and right shift push-pull wires 415 and 416 are connected to a servo valve mechanism 262 for switching the output adjusting swash plate 65a. Either one or both of the left and right traveling hydraulic pumps 65 are controlled to rotate forward by tilting the front of either one or both of the left and right traveling shift levers 43 and 44, and either one or both of the left and right crawler belts 2 are controlled. Is driven forward. On the other hand, one or both of the left and right traveling hydraulic pumps 65 are reversely controlled by a tilting operation to the rear side of either one or both of the left and right traveling shift levers 43, 44, and either one of the left and right crawler belts 2 or Both are driven backwards. In addition, the course of the traveling machine body 1 is changed by changing the amount of tilting operation of the left and right traveling speed change levers 43 and 44, and turning (U-turn) or the like on the field headland is executed.

  Left and right neutral detent ball mechanisms 417 and 418 are detachably connected to the engagement notches 412a and 413b of the left and right lever operation plates 412 and 413, respectively. Left and right neutral detent ball mechanisms 417 and 418 are provided on both sides of the upper frame 281a. When either one or both of the left and right neutral detent ball mechanisms 417 and 418 are engaged with one or both of the left and right lever operation plates 412 and 413, either one of the left and right traveling speed change levers 43 and 44 or Both are configured to be supported in a neutral position (a position where the rotation of the left and right traveling hydraulic pumps 65 is zero).

  As shown in FIGS. 8 and 9, a switch base 421 provided on the front column 281b, a reverse switch 422 provided on the switch base 421, and a reverse sensor arm 423 for operating the switch arm 422a of the reverse switch 422 are provided. A reverse sensor arm 423 is provided on the switch base 421. Further, reverse operation arms 424 are provided on the left and right lever operation plates 412 and 413, respectively. When either one or both of the left and right speed change levers 43 and 44 are operated in reverse, the reverse operation arm 424 is brought into contact with the reverse sensor arm 423 and the reverse switch 422 is operated to notify the reverse operation. ing.

  As shown in FIGS. 8 to 10, a pair of sandwiching plate bodies 427 that sandwich the left and right wire connecting shaft bodies 419 a and 419 b at the same time are provided. One end side of a pair of sandwiching plate bodies 427 is rotatably connected to the upper frame 281a via a pivoting plate body 428. One end side of the pair of tension links 429 is connected to the other end side of the pair of sandwiching plate bodies 427, respectively. One end of a tension rod 430 whose length is adjustable is connected to the other end of the pair of tension links 429. The pedal arm portion of the brake pedal 38 is connected to the other end side of the tension rod 430.

  With the above configuration, when one or both of the left and right traveling speed change levers 43 and 44 are operated to the forward side or the reverse side, by stepping on the brake pedal 38, the pair of tension links 429 and the tension link 429 are pulled. The other end side of the pair of sandwiching plate bodies 427 is pulled downward via the rod 430, and the pair of sandwiching plate bodies 427 is pressed against one or both of the left and right wire connecting shaft bodies 419a and 419b, and the pair of sandwiching plates The left and right wire connecting shaft bodies 419a and 419b are sandwiched by the plate body 427. That is, the traveling speed change levers 43 and 44 are returned from the forward or reverse operation position to the neutral position where the left and right traveling hydraulic pumps 65 rotate to zero. By stepping on the brake pedal 38 (braking operation of the crawler belt 2), both the left and right traveling speed change levers 43 and 44 are supported at the neutral position (position where the vehicle speed becomes zero).

  On the other hand, when the brake pedal 38 is locked to the pedal hook body 283a of the parking lever 283 and the brake pedal 38 is supported at the stepping operation position (position indicated by the phantom line in FIG. 10), the pair of sandwiching plate bodies 427 The left and right wire connecting shaft bodies 419a and 419b are sandwiched. That is, when the crawler belt 2 is braked by the brake operation of the brake pedal 38, both the left and right traveling speed change levers 43, 44 are locked at the neutral position, and the left and right traveling speed change levers 43, 44 are moved forward or backward. Shifting operation that tilts to the side is prohibited.

  Next, the structure of the left and right reduction gear cases 63 as left and right transmission cases for driving the left and right crawler belts 2 will be described with reference to FIG. As shown in FIG. 12, the reduction gear case 63 includes a first housing 301, a second housing 302, and a third housing 303. The first housing 301 is bolted to one end side of the second housing 302, the third housing 303 is bolted to the other end side of the second housing 302, and an appropriate amount of lubricating oil is supplied into the reduction gear case 63 configured in a sealed structure. Put in. A traveling hydraulic motor 69 is disposed on the outer surface of the first housing 301 via an oil passage base body 304. A traveling hydraulic motor 69 is hydraulically connected to the traveling hydraulic pump 65 via an oil passage base 304 and hydraulic piping (not shown). A brake mechanism 297 having a brake lever 296 is provided on one end side of the motor shaft 295 of the traveling hydraulic motor 69. The motor shaft 295 is braked by operating the brake lever 296.

  Further, the other end side of the motor shaft 295 is inserted into the first housing 301 and the second housing 302. A reduction intermediate shaft 308 is pivotally supported on the first housing 301, the second housing 302, and the third housing 303. One end side of the reduction intermediate shaft 308 is connected to the other end side of the motor shaft 305 through a first reduction gear group 309 as the reduction gear mechanism 263. The traveling axle 310 is pivotally supported by the second housing 302 and the third housing 303. The traveling axle 310 is protruded from the third housing 303, and the drive sprocket 51 is pivotally supported on the protruding end portion of the traveling axle 310. The other end side of the reduction intermediate shaft 308 is connected to the traveling axle 310 via the second reduction gear group 311 as the reduction gear mechanism 263.

  With the above configuration, when the traveling hydraulic motor 69 is driven by the traveling hydraulic pump 65, the rotation of the motor shaft 295 is transmitted to the reduction intermediate shaft 308 through the first reduction gear group 309, and the second reduction gear group is transmitted. The rotation of the deceleration intermediate shaft 308 is transmitted to the traveling axle 310 through 311, and the crawler belt 2 is driven forward or backward by the drive sprocket 51.

  Further, as shown in FIGS. 5, 6, 13, and 14, the left traveling hydraulic motor with respect to the left traveling axle 310 in the assembled state in which the reduction gear case 63 is fixed to the rear end portion of the track frame 50. 69 is supported diagonally forward and upward, while the right traveling hydraulic motor 69 is supported obliquely upward and backward relative to the right traveling axle 310. That is, the left and right traveling hydraulic motors 69 are supported at the same height position as the non-grounded side of the crawler belt 2, and the left traveling hydraulic motor 69 is displaced forward with respect to the traveling axle 310 to be supported by the traveling axle 310. On the other hand, the right traveling hydraulic motor 69 is displaced backward and supported.

  As a result, even if the sum of the left and right width dimensions of the two sets of left and right reduction gear cases 63 supporting the traveling hydraulic motor 69 is larger than the installation interval of the reduction gear case 63 between the left and right crawler belts 2, It is attached with the support position shifted back and forth at this position. Further, two sets of left and right reduction gear cases 63 are supported in a gate shape in a rear view (front view). The mud in the field moves through the internal space formed in the gate shape of the left and right reduction gear cases 63, and the traveling movement resistance of the crawler belt 2 is reduced.

  Further, as shown in FIG. 12, a magnet 314 for adsorbing iron powder is placed inside a reduction gear case 63 (first housing 301, second housing 302, third housing 303) as a mission case in which the traveling hydraulic motor 69 is disposed. Is provided. When the first reduction gear group 309 or the second reduction gear group 311 is worn and iron powder is generated in the reduction gear case 63, the iron powder is adsorbed by the magnet 314 and removed. A magnet support holder 315 is integrally formed on the inner surface side of the reduction gear case 63 (first housing 301, second housing 302, third housing 303).

  The magnet support holder 315 is formed in a shape that allows the magnet 314 to be press-fitted and fixed from the molding die cutting direction for molding the reduction gear case 63 (the first housing 301, the second housing 302, and the third housing 303). Further, a plurality of magnets 314 are provided via a plurality of magnet support holders 315 at the bottoms of the respective chambers of the second housing 302 and the third housing 303 or at positions where they are difficult to come off with respect to the traveling direction of the machine. . That is, the magnet support holder 315 can be integrally formed on the bottom (upward plane portion) or the vertical plane portion of the second housing 302 or the third housing 303 by die casting, and the molding die of the second housing 302 or the third housing 303 is formed. The magnet 314 can be easily assembled to the magnet support holder 315 from the extraction opening side. The magnet 314 can be easily assembled in the second housing 302 or the third housing 303 while reducing gear wear due to the iron powder generated in the second housing 302 or the third housing 303. it can.

  Next, the cooling air passage structure of the engine 7 will be described with reference to FIGS. 5, 6, and 15 to 18. A traveling machine body 1 supported by a pair of left and right crawler belts 2 includes a machine body frame 150 formed by connecting a plurality of frames in a substantially lattice shape in plan view. The engine 7 is supported in an anti-vibration manner on the inner side of the engine room frame 56 erected on the right side of the rear portion of the body frame 150. The output shaft 67 of the engine 7 projects from both front and rear side surfaces of the engine 7. An engine output pulley 283 is pivotally supported on the rearward projecting portion of the output shaft 67. A cooling fan 170 is provided at the front projecting portion of the output shaft 67. A radiator 172 for cooling the engine water is disposed in front of the cooling fan 170 via a fan shroud 171.

  A region from the other side of the engine 7 opposite to the threshing device 9 (the right side that is the outside of the machine) to the front of the radiator 172 and the cooling fan 170 is covered with a cover duct body 173. The cover duct body 173 functions as a cooling air path for the engine 7. The outside air is taken in by the cooling fan 170 through the cover duct body 173 (cooling air passage) and the radiator 172, whereby the radiator 172, the engine 7 and the pump case 66 located on the right side of the air are cooled. Will be. This eliminates the need for a cooling structure dedicated to the pump case 66, thereby contributing to cost reduction while maintaining stable driving of the hydraulic system.

  The cover duct body 173 includes a hollow housing side duct 174 located on the right side of the engine 7 and above the pump case 66, and a hollow housing front duct 175 located in front of the radiator 172 and the cooling fan 171. Are configured in a substantially L shape in plan view. The cover duct body 173 (the side duct 174 and the front duct 175) is connected and supported by an engine room frame 56 that surrounds the engine 7. As shown in FIG. 18, the height position of the side duct 174 is set to be higher than the height position of the front duct 175. A plurality of outside air intakes 176 (four in the embodiment) are formed on the right side surface on the outer side of the side duct 174. Each outside air intake 176 is provided with a dustproof filter 177.

  The rear side of the front duct 175 is open. A radiator 172 faces the rear side of the opening of the front duct 175, and an oil cooler 264 is accommodated in front of the opening in the front duct 175. Further, the front duct 175 is provided with a pipe insertion port (not shown) into which a hydraulic pipe connected to the oil cooler 264 is inserted on the left side wall of the accommodation area of the oil cooler 264. Two pipe insertion ports are provided in the left side wall of the front duct 175 so that the hydraulic piping on the upstream side and the downstream side of the oil cooler 264 can be inserted. A sealing member (not shown) is provided on the inner peripheral side of the insertion port so as to seal the outer peripheral surface of the inserted hydraulic pipe.

  Further, as shown in FIG. 6, hydraulic pipes 211 to 215 connected to a pump case 66 disposed on the right side of the engine 7 extend forward on the right side of the engine 7, and the front duct. It is configured to bend at the lower side of 175 and further extend toward the center of the traveling machine body 1. In this way, when the hydraulic pipes 211 to 215 connected to the pump case 66 are arranged to bend from the right side of the engine 7 so as to bypass the front and extend toward the center of the traveling machine body 1, One hydraulic pipe 211 is extended toward the front of the traveling machine body 1 and connected to the oil tank 266. On the other hand, the remaining hydraulic pipes 212 to 214 are bent rearward on the left side of the engine 7 and connected to the oil cooler 264 and the left and right traveling hydraulic motors 69, respectively.

  Thus, since the hydraulic pipes 211 to 215 are installed so as to bypass the front side of the engine 7, the pipes can be installed in an area where no complicated mechanism is arranged, and the assembly work of the hydraulic system can be simplified. Further, since the bypassing hydraulic pipes 211 to 215 on the front side of the engine 7 are arranged so as to pass below the front duct 175, the thermal environment is not severe compared to the inside of the engine room 57. Therefore, the oil flowing in the hydraulic pipes 211 to 215 has a smaller thermal influence from the outside environment, and thus the stable drive of the hydraulic system can be maintained.

  The cover duct body 173 is configured such that the side duct 174 and the front duct 175 can be separated. When the side duct 174 and the front duct 175 are integrated, the left front part of the side duct 174 and the right side part of the front duct 175 communicate with each other. At this time, since the height position of the side duct 174 and the height position of the front duct 175 are different from each other as described above, the air is taken in from the outside air intake port 176 to the lower side of the front portion of the side duct 174. An inclined guide portion 178 inclined obliquely downward and forward is formed so as to guide the cooling air flowing in the lower side of the side duct 175 to the bottom surface side of the front duct 175. Further, on the upper right side of the front duct 175, there is provided an inclined guide portion 179 inclined obliquely downward to the left so as to guide the cooling air flowing through the upper side in the side duct 175 to the front duct 175. Yes. The inclined guide portion 179 on the front duct 175 extends along the right inclined plate 6 b of the Glen tank 6.

  The presence of both the inclined guide portions 178 and 179 makes the side duct 174 and the front duct 175 different from each other even though the height position of the side duct 174 and the height position of the front duct 175 are different. The communication port 180 can be made large in the vertical direction, and the cooling air taken in from the outside air intake port 176 can be smoothly sent from the side duct 174 to the front duct 175.

  In addition, a ring-shaped seal member 187 is fitted to the inner periphery of the opening on the front duct 175 side that forms the communication port 180 at the right end position of the upper inclined guide portion 178. This seal member 187 is formed of an elastic resin material such as rubber or urethane, and when the side duct 174 is connected to the front duct 175, by fitting with the opening of the side duct 174, The confidentiality of the communication port 180 between the side duct 174 and the front duct 175 is enhanced. Further, a fixing plate 192 that contacts the front surface of the front duct 175 is provided on the front surface of the side duct 174 as a fixing member for maintaining the state where the side duct 174 is connected to the front duct 175. The fixing plate 192 is fastened to the front surface of the front duct 175 with a fixing screw 195, so that the opening of the side duct 174 and the opening of the front duct 175 are connected and sealed by the seal member 187. The communication port 180 in the state thus formed is formed.

  The fixing member that fixes the side duct 174 in a state of being connected to the front duct 175 is not limited to the configuration of the fixing plate 192 and the fixing screw 195. That is, for example, a rotatable hook-shaped locking member is provided on the front surface of one of the side duct 174 and the front duct 175, and a pin that the locking member is locked on the other front surface. By providing, the fixing member may be configured as another configuration, for example.

  A shield plate 181 with a punch hole that restricts the intake of cooling air from the two outside air intakes 176 on the front side of the right side surface of the side duct 174 is above the inclined guide portion 178 in the side duct 174. Is arranged. When the shielding plate 181 is disposed at the location, the suction pressure of the cooling air from the two front outside air intakes 176 is suppressed, and as much cooling air as possible is taken in from all the 4 outside air intake ports 176, A sufficient amount of cooling air can be secured while suppressing the wind speed. At this time, by providing the dustproof filter 177 in the outside air intake port 176, it is possible to reduce adhesion of dust such as saw dust accompanying the intake of cooling air.

  As shown in FIG. 6, on the left side surface (side surface on the engine 7 side) 196 of the side duct 174, two frames 197 having a horizontal direction as a longitudinal direction are provided on the upper and lower sides of the side duct 174 so as to project toward the engine room frame 56 side. The The left side 196 is provided with an opening in a region between the frames 197, and a side plate 198 covering the opening is bolted. Further, as shown in FIG. 5, the support bar 188 provided on the right side of the rear portion of the engine room frame 56 is provided with hinge pins 189 at height positions corresponding to the two frames 197 of the side duct 174. . Each of the two hinge pins 189 is inserted into a hinge hole 199 provided on the rear end side of the frame 197.

  With such a configuration, the frame 197 of the side duct 174 is pivotally supported by the hinge pin 189, and the side duct 174 rotates horizontally around the hinge pin 189, so that the engine 7 and the pump case 66 are located on the right side. Open and close. Further, the side duct 174 has a cross-sectional shape that is a substantially triangular shape in plan view with the rear end side as one apex and spreading forward. That is, the side duct 174 is configured such that the apex on the rear end side of the triangle is pivotally supported by a hinge portion formed by a hinge pin 189 and a hinge hole 199 of the frame 197 so as to be horizontally openable and closable. . Therefore, when the side duct 174 is opened, the front portion of the side duct 174 rotates toward the right side (clockwise direction in FIG. 15).

  Thus, by opening the side duct 174 to the outside, the engine room 57 can be opened, so that the engine 7 and the pump case 66 in the engine room 57 can be cleaned and maintenance work for maintenance can be performed. In addition, since the side duct 174 is configured to open from the front, the opening that forms the communication port 180 of the front duct 175 is opened, so that the inside of the duct of the front duct 175 can be easily cleaned. Further, with respect to the side duct 174, not only the opening that forms the communication port 180 is opened, but the side plate 198 on the left side surface 196 is removed to clean the inside of the duct and accompany the intake of cooling air. Dust such as sawdust can be removed.

  As can be seen from FIG. 17, below the side duct 174 is an opening 182 that exposes the arrangement region of the pump case 66 at the lower right side of the engine 7. The opening 182 is covered with a detachable side cover 183. By comprising in this way, the high effect is exhibited in prevention of adhesion of dust, such as sawdust, as much as the height position of the side duct 174 is away from the field. When the side cover 183 is removed, the lower right side of the engine 7 can be exposed, and maintenance work such as cleaning and maintenance of the pump case 66 and the engine 7 can be easily performed. Further, the side cover 183 includes a grip portion (not shown) that responds to an operation on the handle portion 200 provided on the surface thereof. When the side cover 183 is attached, the gripping part is locked to the cover support bar 202 provided on the lower side of the side duct 174 and supported by the side duct 174, and the side cover 183 The lower side is supported by the right side frame of the body frame 150.

  It should be noted that the upper side of the engine 7 is covered with the Glen tank 6 as can be seen from the shape relationship between the inclined guide portion 179 on the front duct 175 and the right inclined plate 6 b of the Glen tank 6. Needless to say, the left side of the engine 7 and the pump case 66 is covered with the threshing device 9.

  As shown in FIGS. 15 and 16, the rear sides of the engine 7 and the pump case 66 are covered with a vertically long plate-like central back cover 185. As shown in FIG. 5, a support frame 190 protrudes rearward from the frame column on the left side of the rear portion of the engine room frame 56, and a hinge pin 191 is provided at the tip of the support frame 190. The center back cover 185 is provided with a frame 203 having a hinge hole 204 at the left end above and below the front surface. The frame 203 is pivotally supported by a hinge pin 191 inserted into the hinge hole 204, whereby the central back cover 185 is configured to be horizontally openable and closable.

  The central rear cover 185 is pivotally supported by a hinge portion composed of a hinge pin 191 and a hinge hole 204 of the frame 203 at the left end thereof, and is configured to be horizontally openable and closable. Therefore, when the center back cover 185 is opened, the right end of the center back cover 185 rotates rearward (clockwise direction in FIG. 15). Thus, when the center back cover 185 is opened and rotated, the driving mechanisms behind the engine 7 and the pump case 66 such as the various belts 230 to 232 and the threshing clutch 233 are exposed. Further, the side duct 174 is pivotally supported on the right rear side of the engine room frame 56, while the central back cover 185 is pivotally supported on the left rear side of the engine room frame 56. Therefore, when the side duct 174 and the center back cover 185 are opened and closed, they can be prevented from interfering with each other.

  Furthermore, the center back cover 185 includes a grip portion 206 that responds to an operation on the handle portion 205 provided on the upper and lower sides on the right side of the front surface. On the other hand, on the upper and lower sides of the support bar 188 on the right rear side of the engine room frame 56, a cover support bar 207 that is engaged with the grip portion 206 is provided. Therefore, when the center back cover 185 is closed, the two gripping portions 206 provided on the right and upper sides of the center back cover 185 are engaged with the cover support bar 207 of the engine room frame 56, so that the center back cover 185 is in the engine room. Supported by the frame 56.

  On the left side of the central back cover 185, a part of the left side of the rear part of the engine room 57 by the engine room frame 56 is covered with a detachable left back cover 186. The left rear cover 186 has a substantially U shape (substantially U shape) in a plan view with the right side surface on the engine room 57 side opened. A cover support bar 208 is provided on the left side surface of the frame 190 provided above and below the left side of the engine room frame 56. The left back cover 186 is supported by the engine room frame 56 by locking the locking member 209 provided on the right back surface thereof with the cover support bar 209.

  A plurality of outside air outlets 193 and 194 with a filter are provided in the center and left rear covers 185 and 186, respectively. Warm air after being blown onto the radiator 172, the engine 7, and the pump case 66 is discharged from the lower part of the body frame 150 and from the outside air outlets 193 and 194 of the center and left rear cover 186.

1 traveling body 2 crawler track (traveling section)
3 Cutting device 7 Engine 9 Threshing device 38 Brake pedal (brake operating tool)
58 Wire support frame 59 Wire support plate 63 Reduction gear case (mission case)
65 Traveling hydraulic pump 69 Traveling hydraulic motor 170 Cooling fan 172 Radiator 173 Cover duct body 174 Side duct 175 Front duct 176 Open air intake 182 Opening 183 Side cover

Claims (4)

A traveling machine body equipped with an engine as a power source, a reaping device having a cutting blade, a threshing device having a handling cylinder, the radiator for cooling the engine water, the cooling fan for cooling the engine and the radiator air, In the combine where the engine is installed on one side of the rear part of the threshing device and the radiator for cooling the engine water and the cooling fan are arranged in front of the engine,
The engine includes a cover duct body that forms a cooling air passage of the engine by covering a region from the other side opposite to the threshing device to the front of the radiator and the cooling fan,
The combine characterized by the side duct body which comprises the side part of this cover duct body being comprised so that opening and closing is possible outside. The cover duct body includes the side duct body, and a front duct body that has an opening communicating with an opening provided on the front left side of the side duct body and covers the front of the engine,
2. The combine according to claim 1, wherein the side duct body is configured to be detachable from the front duct body so that a rear end side thereof is hinged and can be opened and closed from the front side. The height position of the side duct body is set to be higher than the height position of the front duct body, and an outside air intake is formed on the side surface outside the machine in the side duct body,
The lower side of the side duct body is formed in an opening exposing a lower part on the other side of the engine, and the opening is covered with a detachable side cover. Combine. In the left-right width direction of the traveling machine body, a pump case having left and right hydraulic pumps is installed on the right side of the engine, and a left and right hydraulic motor whose braking is controlled by the left and right hydraulic pumps is installed on the left side of the engine,
The hydraulic piping that connects the pump case and the left and right hydraulic motors is piped so as to bypass the front side of the engine below the cover duct body. Combine as described in.

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