WO2012140973A1 - Combine - Google Patents

Abstract

The purpose of the present invention is to provide a combine wherein mud or the like from agricultural fields can be prevented from infiltrating a spline (414) of a travel axle (300) and wear resistance of the spline (414) can be improved. Provided is a combine comprising a travel body (1) equipped with a reaping device (3), a threshing device (9), and an engine (7), a deceleration case (63) being installed in the travel body (1), a drive sprocket (51) for an endless belt (2) being axially supported on the travel axle (300) of the deceleration case (63), and the endless belt (2) mounted on the travel body (1) being driven by the engine (7) via the drive sprocket (51); wherein an axle oil seal (424) is provided between the drive sprocket (51) and an end of the travel axle (300) protruding from the deceleration case (63), and within the travel axle (300), the spline (414) axially supporting the drive sprocket (51) is lubricated.

Description

Combine

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

Conventionally, there is a technology that includes a traveling machine body having left and right crawler belts and a driver's seat, a reaping device, and a threshing device, and continuously chops unmilled cereals in the field (Patent Document 1). A technique for driving the left and right crawler belts by operating the left and right traveling hydraulic motors with left and right traveling hydraulic pumps is also known (see Patent Document 2).

Japanese Patent No. 4179950 Japanese Utility Model Publication No. 49-125442

The conventional technique disclosed in Patent Document 1 includes a hydraulic pump and a hydraulic motor that drive a traveling crawler. Since a hydraulic motor is provided on the inner circumference side of the traveling crawler and the hydraulic motor and reducer are arranged on the axis of the drive sprocket, the drive sprocket and reducer must be provided on the track frame via the hydraulic motor housing. There is a problem that the cost cannot be easily reduced. In the prior art disclosed in Patent Document 2, a hydraulic motor is provided outside the traveling crawler and a speed reducer case is provided on the track frame. A part of the speed reducer case forms a shaft that supports the drive sprocket. Therefore, there is a problem that muddy water easily enters from the bearing portion of the drive sprocket.

Therefore, the present invention seeks to provide an improved combine by examining these current conditions.

In order to achieve the above object, a combine according to a first aspect of the present invention includes a traveling machine body on which a reaping device, a threshing device, and an engine are mounted. In a combine that drives a crawler belt mounted on the traveling body by the engine via the drive sprocket, the axle end projecting from the speed reduction case, the drive sprocket, An oil seal body for an axle is provided between the two, and the spline portion on which the drive sprocket is pivotally supported is lubricated.

According to a second aspect of the present invention, in the combine according to the first aspect, a bearing oil seal and a bearing seal collar are provided on the axle, and the boss portion of the drive sprocket is provided in the axial direction of the axle. The bearing seal collar is integrally formed at one end of the boss portion.

According to a third aspect of the present invention, in the combine according to the second aspect, the bearing seal collar is fitted on a portion of the axle that is separated from a spline portion on which the drive sprocket is pivotally supported. .

According to a fourth aspect of the present invention, in the combine according to the first aspect, a bearing oil seal and a bearing seal collar body are provided on the axle, and the drive sprocket and the bearing seal collar body are separately formed. A collar oil seal body is provided between the drive sprocket and the bearing seal collar body.

According to a fifth aspect of the present invention, in the combine according to the first aspect, the left and right shift levers are operated to control the transmission to a forward output state or a reverse output state, and the left and right sides from the engine via the transmission are controlled. Each of which has a structure for transmitting a driving output to each of the crawler belts, and includes a check means for restricting the transmission control of the other transmission lever by the transmission control of one of the left and right transmission levers. The maximum shift range of the reverse operation of the other shift lever is limited by the forward or reverse operation.

According to a sixth aspect of the present invention, in the combine according to the fifth aspect of the present invention, the left and right transmissions that are independently controlled to the forward output state or the reverse output state by operating the left and right shift levers are provided. When either one of the left and right transmissions is controlled near the maximum forward output, the reverse transmission can be output within a certain range from the other transmission.

According to a seventh aspect of the present invention, in the combine according to the fifth aspect, a check arm body is provided as the check means, the check arm body is connected to one or both of the left and right shift levers, and the one When the other shift lever is operated, the operable range of the other shift lever is limited by the check arm body, whereas when the other shift lever is operated, the operable range of the one shift lever is It is configured to be restricted by the check arm body.

According to an eighth aspect of the present invention, in the combine according to the fifth aspect, vehicle speed control means is provided as the restraining means, and the other speed change lever is controlled by forward control or reverse control of the vehicle speed control means by the one speed change lever. The maximum shift output of the reverse control of the vehicle speed control means is limited.

According to the first aspect of the present invention, there is provided a traveling machine body on which a reaping device, a threshing device, and an engine are mounted, a deceleration case is installed on the traveling machine body, and a drive sprocket for a crawler belt is provided on the axle of the deceleration case. Axle oil is supported between the drive sprocket and the axle end projecting from the deceleration case in a combine that drives the crawler belt mounted on the traveling machine body via the drive sprocket by the engine. Since the seal body is provided to lubricate the spline portion on which the drive sprocket is pivotally supported among the axles, it is possible to easily prevent mud in the field from entering the spline portion. The wear resistance of the part can be easily improved. Further, in the structure in which the bearing oil seal is provided in the bearing bearing portion on the axle via the bearing seal collar, the surface pressure on the bearing side end face of the bearing seal collar is lowered, and the wear resistance of the bearing seal collar is improved. In addition, the axle torque can be easily secured.

According to a second aspect of the present invention, a bearing oil seal and a bearing seal collar are provided on the axle, and the boss portion of the drive sprocket extends in the axial direction of the axle, and the boss Since the bearing seal collar is integrally formed at one end of each part, the number of components of the bearing part of the drive sprocket can be reduced to reduce the manufacturing cost, and the assembly workability of the drive sprocket and the like can be improved. it can.

According to the third aspect of the present invention, since the bearing seal collar is fitted to a portion of the axle that is removed from the spline portion on which the drive sprocket is pivotally supported, the diameter of the drive sprocket is The backlash in the direction can be easily reduced, and the load resistance of the drive sprocket can be easily improved.

According to a fourth aspect of the present invention, there is provided a structure in which a bearing oil seal and a bearing seal collar body are provided on the axle, and the drive sprocket and the bearing seal collar body are separately formed. Since the collar oil seal body is provided between the bearing seal collar body and the bearing seal collar body, it is easy for mud in the field to enter the spline portion between the drive sprocket and the bearing seal collar body. The wear resistance of the spline portion can be easily improved. Further, the surface pressure on the bearing side end face of the bearing seal collar body can be lowered to improve the wear resistance, and the axle torque can be easily secured.

According to the fifth aspect of the present invention, the transmission is controlled to the forward output state or the reverse output state by operating the left and right shift levers, and the driving drive output is output from the engine to the left and right crawler tracks via the transmission. Each of the transmission structures has a check means for restricting transmission control of the other transmission lever by transmission control of one of the left and right transmission levers, and by forward operation or reverse operation of one transmission lever. Since the maximum shift range of the reverse operation of the other shift lever is limited, for example, a harvesting device that harvests uncut cereal grains in the field and grain of the harvested cereal grains In a combine equipped with a threshing device, when harvesting cereal grains in a field by reciprocating movement, it is possible to improve the direction changing workability in a field headland where the frequency of forward / reverse switching is high. Further, even if a shift lever is provided so that the speed can be changed to the maximum forward speed or the maximum reverse speed, a sudden increase in traveling load can be easily prevented. Therefore, engine troubles can be reduced and steering performance can be improved.

According to a sixth aspect of the present invention, there is provided a structure including left and right transmissions that are independently controlled to a forward output state or a reverse output state by operating the left and right shift levers. When either one is controlled near the maximum forward output, the reverse transmission can be output within a certain range from the other transmission. ), The other crawler belt can be driven with a reverse output (or forward output) below a predetermined value. That is, the crawler track outside the turn can be driven at the maximum output while the crawler track inside the turn is driven in reverse. Mobility according to road surface conditions (dry fields, wet fields, traveling on the road, etc.) can be obtained.

According to the seventh aspect of the present invention, when a check arm body is provided as the check means, the check arm body is connected to one or both of the left and right speed change levers, and the one speed change lever is operated. In addition, the operable range of the other shift lever is limited by the check arm body, while the operable range of the one shift lever is limited by the check arm body when the other shift lever is operated. Thus, the restraining arm body can be compactly assembled to the mounting portions of the left and right speed change levers. The shift operation structure can be simplified and the manufacturing cost can be reduced. For example, in a structure in which the left and right crawler belts are respectively driven by the left and right hydraulic pumps constituting the left and right transmission, the shift operation structure provided between the swash plate control unit of the left and right hydraulic pump and the left and right transmission levers can be simplified.

According to the invention described in claim 8, vehicle speed control means is provided as the restraining means, and the reverse direction of the vehicle speed control means by the other speed change lever by forward control or reverse control of the vehicle speed control means by the one speed change lever. Since the maximum shift output of the control is limited, even if the vehicle moves at the maximum forward speed or the maximum reverse speed, a sudden increase in travel load can be easily prevented. Mobility according to road surface conditions (dry fields, wet fields, traveling on the road, etc.) can be obtained.

It is a left view of a combine. 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 left view of a traveling body. It is a top view of a traveling body. It is the perspective view which looked at the cab from the front. It is a hydraulic circuit diagram of a combine. It is a side view of a traveling gear shift lever attaching part. It is the perspective view which looked at the traveling shift lever attachment part from the front. It is the perspective view which looked at the traveling shift lever attachment part from back. It is an enlarged side view of a travel drive part. It is the perspective view which looked at the cutting posture lever attachment part of the steering column from the front. It is the expansion perspective view which looked at the cutting posture lever attachment part of the steering column from back. It is the perspective view which looked at the working clutch lever attachment part of the steering column from the front. It is the perspective view which looked at the working clutch lever attachment part of the steering column from back. It is the perspective view which looked at the threshing clutch attachment part from the front. It is principal part expansion explanatory drawing of FIG. It is a side view which shows the deformation | transformation structure of a work clutch lever attaching part. It is a plane explanatory view in which a travel shift lever is in a neutral position. FIG. 6 is an explanatory plan view of a travel shift lever that is operated forward. It is plane explanatory drawing which left-turned the travel shift lever. FIG. 6 is an explanatory plan view of a travel shift lever that is turned right. It is explanatory drawing which carried out the left spin turn operation of the travel shift lever. It is plane explanatory drawing which carried out the right spin turn operation of the travel shift lever. FIG. 21 is an explanatory plan view showing a first modification of the check structure which is the modified structure of FIG. 20. It is the control circuit which provided the vehicle speed controller which shows a 2nd modification. It is a hydraulic circuit diagram which shows a 2nd modification. It is a flowchart of the vehicle speed control which shows a 2nd modification. It is a left view of the drive part of a threshing apparatus. It is the perspective view which looked at the drive part of the threshing device from back. It is the perspective view which looked at the drive part of the threshing device from the front. It is a rear view of the drive part of a combine. It is a side view of the traveling drive part of a combine. It is the perspective view which looked at the traveling drive part from the front. It is the perspective view which looked at the traveling drive part from back. It is a top view of the traveling drive part. It is an enlarged plan view of the traveling drive unit. It is sectional drawing of a reduction gear case. It is principal part sectional drawing of a reduction gear case. It is a partial expanded sectional view of a reduction gear case. FIG. 42 is an exploded explanatory diagram of FIG. 41. It is a partial expanded sectional view of the reduction gear case which shows the 1st modification of a travel axle support structure. FIG. 44 is an exploded explanatory diagram of FIG. 43. It is a partial expanded sectional view of the reduction gear case which shows the 2nd modification of a travel axle support structure. It is a whole rear view which shows the combine which concerns on 2nd Embodiment. It is a side view which shows the traveling apparatus of a combine. FIG. 2A is a side view showing a footwear plate in a combine traveling device, FIG. 2B is a bottom view showing a footwear plate in a combine traveling device, and FIG. 3C is a perspective view showing a footwear plate in the combine traveling device. It is a fragmentary sectional view of the traveling device of a combine. It is a whole rear view which shows the combine which concerns on 3rd Embodiment. It is a side view which shows the traveling apparatus of a combine. FIG. 2A is a side view showing a footwear plate in a combine traveling device, FIG. 2B is a bottom view showing a footwear plate in a combine traveling device, and FIG. 3C is a perspective view showing a footwear plate in the combine traveling device. (A) The partial side view at the time of making a drive sprocket small in the traveling apparatus of a combine, (b) The partial side view at the time of making the bending length of a footwear board long in the traveling apparatus of the combine which concerns on other embodiment.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings (FIGS. 1 to 3) applied to an ordinary 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, a schematic structure of a combine will be described with reference to FIGS. 1 to 3. 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 tracks 2 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.

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 conveyor 8 (discharge auger) is provided so as to be rotatable. The grain in the Glen tank 6 is configured to be carried out from the pallet throwing port 8a at the tip of the grain discharge conveyor 8 to, for example, a truck bed or a container. 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 handling port 9a in the front part of the threshing device 9 and a horizontally long bucket-shaped grain header 12 that is provided continuously at 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. Further, under the control of the reel lifting / lowering hydraulic cylinder 251 described later, the take-up reel 14 moves up and down around the reel lifting / lowering fulcrum shaft 250.

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 FIG. 1 thru | or FIG. 3, the handling cylinder 21 is rotatably provided in the handling chamber of the threshing apparatus 9. 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.

In addition, a plurality of dust feeding valves (not shown) for adjusting the conveying speed of threshing 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 which has been threshed by the handling cylinder 21 and leaked from the receiving net 24 is selected by the specific gravity selection action of the swinging sorter 26 and the wind sorting action of the tang fan 29, and the first sort (grain etc.) and sorting. It is configured to be sorted into second items (grains and the like mixed with branch rafts) and sorted third items (such as sawdust).

The first conveyor mechanism 30 and the 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 front column 41a as the control column 41 is provided with a cutting posture lever 45 for raising and lowering the cutting device 3 by tilting in the front-rear direction and raising and lowering the take-up reel 14 by tilting in the left and right direction, and rotation of the engine 7. An accelerator lever 46 to be controlled and a grain discharge lever 47 for moving the grain discharge conveyor 8 up and down are arranged. A horizontal movement switch 37 for turning the grain discharge conveyor 8 is provided on the rear side of the grain discharge lever 47. A guard frame 5a that is gripped when the operator who sits on the driver's seat 42 is in a standing posture extends 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. The support column 48 and an auger rest 8b described later are fixed to the front wall of the glen tank 6.

Also, the side column 41b as the steering column 41 is provided with left and right traveling speed change levers 43 and 44 as speed change operating tools (steering levers) for changing the course of the traveling machine body 1 and changing the moving speed. As shown in FIG. 7, at the rear end of the side column 41b, there is a cutting clutch lever 39 (working clutch lever) for turning on and off the power transmission of the cutting device 3, and a threshing clutch lever for turning on and off the power transmission of the threshing device 9. 40 (work clutch lever) is arranged. Further, a brake pedal 38 for crawler belt 2 braking is provided below the front portion of the side column 41b.

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 23, the ground side of the crawler belt 2 is supported by the track roller 53, and the non-ground side of the crawler belt 2 is supported by the intermediate roller 54 To be configured.

Also, as shown in FIGS. 1 to 3, a bottom feed conveyor 60 disposed at the bottom of the Glen tank 6 and a vertical feed conveyor 61 disposed at the rear 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 conveyor 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 tip (feeding end side) of the discharge conveyor 8.

The feed start end of the grain discharge conveyor 8 is supported on the upper end side of the vertical feed conveyor 61 so as to be rotatable in the vertical direction. The cocoon throwing port 8a side which is a feed terminal part of the grain discharge conveyor 8 is configured to be movable up and down. In addition, it is configured such that the side of the throwing hole 8a can be moved around the conveyor shaft center (horizontal direction) of the vertical feed conveyor 61. That is, the hull throwing port 8a side is moved to the front lower side of the traveling machine body 1, and the grain discharge conveyor 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 feed discharge end of the grain discharge conveyor 8 is raised on the side of the spear spout 8a, and the spear spout 8a is moved to the side or the rear of the traveling machine body 1 so The discharge conveyor 8 is protruded, the pallet throwing port 8a is opposed to 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. As shown in FIG. 4 to FIG. 6, a travel speed change pump case 66 having a pair of swash plate variable left and right travel 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 left side of the engine 7. Also, left and right reduction gear cases (reduction 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 an engine output belt 231. 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 pump case 66 is disposed between the engine 7 and the threshing device 9.

A charge pump 68 that supplies hydraulic oil to a closed-loop hydraulic circuit 261 (a hydraulic circuit that connects the traveling hydraulic motor 69 to the traveling hydraulic pump 65), which will be described later, is also provided on the same axis 64 as the traveling hydraulic pump 65. Further, a working hydraulic pump 70 for operating the lifting hydraulic cylinder 4 or the horizontal control hydraulic cylinder 19 is disposed in the engine 7, and the charge pump 68 and the working hydraulic pump 70 are connected to the engine 7 in the same manner as the traveling hydraulic pump 65. It is comprised so that it may drive.

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, 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, respectively. The left and right crawler belts 2 are driven in the forward or backward direction by the left and right traveling hydraulic motor 69 via the drive sprocket 51. The operator operates the left and right traveling speed change levers 43 and 44 to adjust the swash plate angles (shift control) of the left and right traveling hydraulic pumps 65, whereby the rotational speed or rotational direction of the left and right traveling hydraulic motors 69 can be adjusted. The left and right crawler belts 2 are driven independently from each other, and the traveling machine body 1 is configured to move forward, backward, or turn.

As shown in FIG. 4, a barrel driving case 71 that supports a threshing input shaft 72 is provided. A threshing input shaft 72 is connected to a travel drive input shaft 64 as a counter shaft via a threshing drive belt 232. The power of the engine 7 is transmitted from the travel drive input shaft 64 to the threshing input shaft 72 via a tension roller 233 as a threshing clutch and a threshing drive belt 232. The threshing clutch 233 is controlled to be turned on and off by the operation of the threshing clutch lever 40 by the operator. Further, a threshing input shaft 72 is connected to one end side (rear end side) of the barrel 20 via a barrel drive belt 234. By the turning-on / off operation of the threshing clutch 233, the handling cylinder 21 is driven and controlled via the threshing input shaft 72, and the cereal straw thrown from the beater 18 is continuously threshed by the handling cylinder 21.

Furthermore, 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. The 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 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. To the left end of the first conveyor shaft 77 of the first conveyor mechanism 30 and to the left end of the second conveyor shaft 78 of the second conveyor mechanism 31, a tang shaft 76 is connected via a conveyor drive belt 237 (selection drive belt). Are connected. The left end portion of the second conveyor shaft 78 is connected to the left end portion of the crank-shaped swing drive shaft 79 that pivotally supports the rear portion of the swing sorter 26 via the swing sorting belt 236 (sorting drive belt). . The cereal conveyor 32 is driven via the first conveyor shaft 77, and the first selected item (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 sorted product (grains mixed with swarf) of the second conveyor mechanism 31 returns to the upper surface side of the swing sorter 26. And sorted again.

On the other hand, the left end of the beater shaft 82 is connected to the left end of a cutting input shaft 89 on which the feed end side of the supply conveyor 17 is pivotally supported via a cutting drive belt 241 and a tension roller type cutting clutch 242. is doing. 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.

As shown in FIGS. 1 and 4, the engine 7 is mounted on the rear part of the traveling machine body 1, and the power of the engine 7 is transmitted to the rear end side of the handling cylinder shaft 20 on which the handling cylinder 21 is pivotally supported. The power of the engine 7 is transmitted from the front end side of the engine 20 to the cutting device 3 and the beater 18, the beater 18 is driven via the barrel shaft 20, and the cutting device 3 is driven via the beater 18. Therefore, by arranging the engine 7 at the rear part of the traveling machine body 1, the front-rear balance of the traveling machine body 1 can be improved, and the large reaping device 3 having a wide cutting width can be stably supported. That is, it is possible to improve harvesting workability in wet fields or mobility on rough roads. Further, since the power of the engine 7 is transmitted to the beater 18 and the reaping device 3 using the handling cylinder 20, even if the reaping device 3 and the engine 7 are provided apart from each other, the engine 7 is connected to the beater 18 or the reaping device 3. The transmission path can be easily configured. That is, the maintenance workability of the drive structure such as the reaping device 3 or the threshing device 9 can be improved.

As shown in FIGS. 4, 30, and 32, the threshing device 9 is provided with a grain sorting mechanism 10, and a sorting input belt as a sorting drive belt of the grain sorting mechanism 10 is provided on the front end side of the barrel shaft 20. 235, the swing sorting belt 236, and the conveyor drive belt 237 are connected to transmit the power of the engine 7 from the front end side of the barrel shaft 20 to the grain sorting mechanism 10. It is possible to simplify the drive input structure of the grain sorting mechanism 10 that transmits For example, the sorting input belt 235, the swing sorting belt 236, and the conveyor drive belt 237 can be shortened as compared with a structure in which the power of the engine 7 is transmitted to the grain sorting mechanism 10 without using the barrel shaft 20. In the grain sorting mechanism 10, power can be transmitted from the engine 7 at the rear of the traveling machine body 1 to each sorting input unit in order from the sorting input unit on the high rotation side (the Chinese fan 29). The plurality of input parts of the grain sorting mechanism 10 can be arranged and driven in order from the high rotation side (the tang fan 29), with almost no restriction on the installation position of the engine 7. For example, the Kara fan 29, the first conveyor mechanism 30, the second conveyor mechanism 31, the swing sorter 26, etc. are rotated at an appropriate rotation speed by a small number of sort input belts 235, swing sort belts 236, and conveyor drive belts 237. Can operate.

As shown in FIGS. 4, 30, and 32, the threshing device 9 is provided with a grain sorting mechanism 10, and the grain tank 6 is arranged on one side of the threshing device 9, and the other side of the threshing device 9 The cutting drive belt 241 that transmits power to the cutting device 3 and the sorting input belt 235, the swing sorting belt 236, and the conveyor driving belt 237 that transmit power to the grain sorting mechanism 10 are extended in the longitudinal direction. Therefore, replacement or maintenance work of the cutting drive belt 241 or the sorting input belt 235, the swing sorting belt 236, the conveyor driving belt 237, etc. can be easily performed from the side of the machine body opposite to the Glen tank 6 installation side. . Since it is not necessary to secure the installation space of the drive belt mechanism on both the left and right sides of the reaping device 3 and the threshing device 9, the arrangement structure of the engine 7 or the threshing device 9 is not restricted to each other, and the reaping drive belt 241 or the selection input belt 235 is provided. The swing sorting belt 236, the conveyor drive belt 237 and the like can be easily replaced, and the maintenance workability of the drive belt structure can be improved. Further, it is not necessary to secure an installation space for the sorting input belt 235, the swing sorting belt 236, the conveyor drive belt 237, etc. between the threshing device 9 and the Glen tank 6, and the threshing device 9 and the Glen tank 6 are arranged close to each other. It is possible to improve the balance of the traveling body 1 in the left-right direction or the front-rear direction.

Further, as shown in FIG. 4, the rear end side of the bottom feed conveyor shaft 103 of the bottom feed conveyor 60 is connected to the rear end portion of the travel drive input shaft 64 via the grain discharge belt 244 and the grain discharge clutch 245. Let One end side of the lower mediation shaft 105 is connected to the rear end portion of the bottom feed conveyor shaft 103 via a longitudinal feed drive chain 104. The other end side of the mediation 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 conveyor 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 conveyor 8 are driven and controlled by turning on and off the grain discharge clutch 245 so that the grains in the grain 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 rides on the saddle cradle 223 in a state where the saddle cradle 223 is supported in a horizontal working posture, and attaches a saddle bag to a saddle catcher (not shown). 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. That is, by discharging the grain in the grain tank 6 from the grain outlets 221, 222, the grain in the grain tank 6 can be discharged without interrupting the mowing and threshing operation. Compared with the work of discharging the grain in the grain tank 6 from the grain discharge conveyor 8 to the truck bed outside the field, there is almost no need to interrupt the mowing and threshing work, so the time for interrupting the mowing and threshing work in the harvesting work ( The time for moving between the mowing place and the truck bed can be shortened, and the harvesting work efficiency can be improved.

Next, the combine hydraulic structure will be described with reference to FIG. As shown in FIG. 8, as the hydraulic actuator, the cutting lift 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 to be movable up and down, and the grain An auger lifting hydraulic cylinder 252 that moves up and down the discharge conveyor 8. The working hydraulic pump 70 is hydraulically connected to the horizontal control hydraulic cylinder 19 through a horizontal control electromagnetic hydraulic valve 253 that is controlled by operation of the horizontal control switch 254. The operator operates the horizontal control switch 254 to activate the horizontal control hydraulic cylinder 19, thereby maintaining the horizontal inclination of the reaping device 3 at a horizontal or arbitrary inclination. As shown in FIG. 7, a horizontal control switch 254 is provided at the upper end of the cutting posture lever 45.

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. is 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 actuated, and the operator moves the cocoon throwing port 8a of the grain discharging conveyor 8 up and down to an arbitrary height. In addition, by operating the horizontal movement switch 37 and causing an electric motor (not shown) to perform forward / reverse operation, the grain discharge conveyor 8 is pivoted in the horizontal direction, and the culling spout 8a is moved in the horizontal direction. That is, it is configured such that the culling spout 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. 8, 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 traveling speed change levers 43 and 44 are connected to the output adjustment swash plate 65a of the left and right traveling hydraulic pump 65 via the servo valve mechanism 262, respectively, so that the left and right traveling speed change levers 43 and 44 are inclined in the front-rear direction. The support angle of the output adjustment swash plate 65a is changed proportionally. 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 configured to be driven forward or backward.

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

In other words, the inclination angle of the left and right speed change levers 43, 44 at a vehicle speed proportional to the inclination angle of the left and right travel speed change levers 43, 44 by making the operation amount or direction of the left and right travel speed change levers 43, 44 different. The traveling machine body 1 can be turned in the left-right direction with a turning radius proportional to the difference between the two. 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 left and right closed loop hydraulic circuits 261 are supplied with hydraulic oil in the oil tank 266. It is configured. A brake mechanism 297 having a brake brake lever 296 is provided on the motor shaft 295 of the traveling hydraulic motor 69. The motor shaft 295 is configured to be braked by operating the brake braking lever 296.

Next, the mounting structure of the brake pedal 38 and the travel shift levers 43 and 44 will be described with reference to FIGS. As shown in FIGS. 9 to 12, 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.

As shown in FIGS. 9 to 11, 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 for supporting 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 FIG. 12, the brake wire 278 is provided with a brake link 286 that connects the upper end side via a brake spring 285. An intermediate portion of the brake link 286 is pivotally supported on the traveling machine body 1 via a link support shaft 287. A lower end side of the brake link 286 is connected to a brake braking lever 296 provided in the left traveling hydraulic motor 69 via a pin shaft body 288 and a long hole 289. Also, a brake brake lever 296 provided on the right traveling hydraulic motor 69 is connected to the pin shaft body 288 via a bolt shaft body 290 and a connection shaft body 291 whose connection length can be adjusted.

Furthermore, as shown in FIG. 12, a lever return stopper body 292 that supports the brake brake lever 296 at the brake release position, and a brake release spring 293 that supports the brake brake lever 296 in contact with the lever return stopper body 292 are provided. A lever return stopper body 292 is provided on the left traveling hydraulic motor 69, and a brake release spring 293 is connected between the brake braking lever 296 provided on the left traveling hydraulic motor 69 and the lever return stopper body 292. When the brake pedal 38 is stepped on, the brake mechanism 297 provided on the left and right traveling hydraulic motors 69 operates in a braking state. On the other hand, the brake state of the brake mechanism 297 is released by the brake release spring 293 in a state where the stepping portion 38a of the brake pedal 38 is supported at the raised position.

As shown in FIGS. 9 to 11, a shift lever fulcrum shaft 411 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 281a of the side column frame 281 forming the side column 41b. 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 removably 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. Note that, when the operation load is equal to or greater than the engaging force of the interlocking detent ball mechanism 414, only one traveling speed change lever 43 or 44 on the operated side operates.

Further, one end sides of the left and right shift push- pull wires 415 and 416 are connected to the lower end sides of the left and right lever operation plates 412 and 413 via the left and right wire connecting shaft bodies 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 speed change 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 that are detachably connected to the engagement notches 412a and 413b of the left and right lever operation plates 412 and 413 are provided. 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 at a neutral position (a position where the rotation of the left and right traveling hydraulic pumps 65 is zero).

As shown in FIGS. 9 and 10, 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 FIG. 9 to FIG. 11, a pair of clamping plate bodies 427 that simultaneously clamp the left and right wire connecting shaft bodies 419a and 419b 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. 9), 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.

As shown in FIGS. 1 and 9 to 11, the reaping device 3, the threshing device 9 having a handling cylinder 21, and the traveling machine body 1 having a driving seat 42 are provided, and cereals are supplied from the reaping device 3 to the threshing device 9. In the combine, the harvesting posture lever 45 is provided as a harvesting operation lever in the steering column 41 in front of the driver seat 42, and left and right traveling speed change levers 43, 44 are provided in the steering column 41 on the side of the driver seat 42. The left and right traveling units 2 can be controlled by operating the shift levers 43 and 44, respectively. Therefore, the operator sitting on the driver's seat 42 can switch the left and right traveling shift levers 43 and 44 by left hand operation, and the cutting posture lever 45 can be switched by the right hand operation of the operator, thereby improving the maneuverability. . For example, in a structure in which the take-up reel 14 is provided, the operator can operate the cutting posture lever 45 with the right hand to move the take-up reel 14 up and down while raising and lowering the cutting device 3, while the operator moves the left and right with the left hand. The vehicle speed (movement speed) can be changed by a speed change operation while operating the travel speed change levers 43 and 44 and changing the course by a left and right turning operation. The cutting posture operation of the cutting device 3 provided with the take-in reel 14 or the like can be simplified. It is possible to improve the cutting workability in a field that requires a vehicle speed (moving speed) change operation or a course change operation, such as a field where grain cereals are partially lying down.

As shown in FIG. 1, FIG. 4, FIG. 8, and FIG. 9 to FIG. 12, a reaping device 3, a threshing device 9 having a handling cylinder 21, and a traveling machine body 1 having crawler belts 2 as left and right traveling parts are provided. The combine that supplies the cereal meal from the device 3 to the threshing device 9 has a structure in which a reduction gear case 63 as a left and right reduction case for independently driving the left and right crawler belts 2 is provided. Since the brake mechanisms 297 are respectively arranged, and the left and right brake mechanisms 297 are connected to the brake pedal 38 as a single brake operation tool of the cab 5 as the driving operation unit. The brake mechanism 297 can be operated simultaneously, and the left and right crawler belts 2 can be braked simultaneously. The traveling machine body 1 can be stopped without changing the moving direction (the course) of the traveling machine body 1. Further, for example, even if the brake pedal 38 and the left and right brake mechanisms 297 are installed separately from the front and rear parts of the traveling machine body 1, the braking operation structure of the left and right crawler belts 2 can be reduced in cost. It can be configured simply.

As shown in FIGS. 5, 6, and 12, the left and right traveling hydraulic motors 69 provided in the left and right reduction gear cases 63 are arranged with their installation positions shifted in the front-rear direction of the traveling machine body 1. A brake link 286 as a brake brake lever is provided in the traveling machine body 1 located in the middle, and a brake as a brake operation tool is provided via a brake link 286 to the left and right brake mechanisms 297 provided on the left and right traveling hydraulic motor 69 axes. Since the pedal 38 is connected, the left and right traveling hydraulic motors 69 can be arranged close to each other in the left-right width direction of the traveling machine body 1, and the traveling unit braking operation structure for connecting the brake pedal 38 to the left and right brake mechanisms 297. Can be configured at low cost and simply. For example, the brake pedal 38 at the front part of the traveling machine body 1 and the left and right brake mechanisms 297 at the rear part of the traveling machine body 1 can be easily connected by a single brake wire 278 that brakes the left and right brake mechanisms 297. The braking force of the brake mechanism 297 can be easily adjusted, and the maintenance workability can be improved.

As shown in FIGS. 9 to 11, the left and right traveling speed change levers 43 and 44 are provided on the cab 5, and the left and right traveling speed change levers 43 and 44 are operated by stepping on the brake pedal 38 as a brake operating tool. Thus, the left and right crawler belts 2 can be braked by setting the travel shift to neutral (the travel drive output is zero) only by the braking operation of the brake pedal 38. It is possible to prevent the traveling hydraulic pump 65 or the traveling hydraulic motor 69 from being overloaded by eliminating the difference between the timing for returning the left and right traveling shift levers 43 and 44 to the neutral position and the timing for braking the left and right crawler belts 2. Further, it is possible to simplify the hydraulic structure for driving the crawler belt 2 incorporating the traveling hydraulic pump 65 or the traveling hydraulic motor 69, or the operation for stopping the left and right crawler belts 2 and the like. That is, while the manufacturing cost of the hydraulic structure for driving the crawler belt 2 can be easily reduced, handling operability such as maintenance of the hydraulic structure for driving the crawler belt 2 can be improved. Further, an emergency stop can be performed by omitting the neutral return operation of the left and right traveling speed change levers 43 and 44, and the slippage of the crawler belt 2 or the excavation of a farm scene can be reduced.

Next, with reference to FIG. 7, FIG. 8, FIG. 13, FIG. 14, and FIG. 18, the mounting structure of the cutting posture lever 45 and the grain discharge lever 47 will be described. As shown in FIGS. 13, 14, and 18, a lever fulcrum chassis 441 is fixed to the inner surface of the front column 41 a that is erected from the cab 5. The lever fulcrum frame 442 is bolted to the lever fulcrum chassis 441. A left / right rotation fulcrum shaft 443 is fixed to the lever fulcrum frame 442. A left-right rotation frame 444 is provided that is supported to be rotatable about a left-right rotation fulcrum shaft 443 extending in the front-rear direction of the machine body. The left and right rotation boss 444a and the front and rear rotation boss 444b are integrally fixed to the left and right rotation frame 444.

Also, the left and right rotation boss 444a is pivotally supported on the left and right rotation fulcrum shaft 443. A front / rear rotation fulcrum shaft 445 is pivotally supported on the front / rear rotation boss 444b. A base end portion of the cutting posture lever 45 and an upper end portion of the front / rear rotation frame 446 are integrally fixed to a front / rear rotation fulcrum shaft 445 extending in the left-right direction of the machine body. A lower end portion of a front / rear rotation frame 446 extending directly below the left / right rotation fulcrum shaft 443, and a bar frame-shaped spring support 447 extending from the lever fulcrum frame 442 to a position directly below the left / right rotation fulcrum shaft 443; In between, the lever return spring 448 which connects the cutting posture lever 45 back to an upright posture is connected.

On the other hand, as shown in FIGS. 13, 14 and 18, a fulcrum side frame 453 for fixing one end side to the lever fulcrum frame 442 is provided. The lever fulcrum boss portion 453a is integrally fixed to the fulcrum side frame 453. The base end portion 47a of the grain discharge lever 47 is passed through the fulcrum side frame 453 and the lever fulcrum boss portion 453a, and the grain discharge lever 47 is pivotally supported by the lever fulcrum boss portion 453a so as to be rotatable in the front-rear direction. An intermediate portion of an L-shaped cutting lift link 454 is rotatably supported on the base end portion 47 a of the grain discharge lever 47.

Furthermore, a vertically long locking groove 446 a is formed on the lower end side of the front / rear rotating frame 446. An engagement shaft body 455 is provided on one end side of the L shape of the cutting lift link 454, and the engagement shaft body 455 is slidably engaged in the locking groove 446a. The upper end side of the plate-shaped cutting rod lifting / lowering cooperative rod body 456 is connected to the L-shaped other end side of the cutting lifting link 454. The lower end side of the cutting / lifting cooperation rod body 456 is connected to the cutting lifting / lowering spool 255a of the manual lifting / lowering hydraulic valve 255. That is, by turning the cutting posture lever 45 around the pivot shaft 445 and tilting the cutting posture lever 45 in the longitudinal direction of the machine body, the cutting lifting link 454 is moved around the base end portion 47a of the grain discharge lever 47. Rotating and moving the cutting rod lifting / lowering linkage rod body 456 up and down to operate the cutting and lifting spool 255a, switching the cutting and lifting manual hydraulic valve 255, operating the lifting and lowering hydraulic cylinder 4, and lifting and lowering the cutting device 3 It is configured to move.

Also, the upper end side of the plate-shaped reel ascending / descending cooperation rod body 458 is connected to the left / right rotation frame 444 via the pivot shaft 457. The lower end side of the reel lifting / lowering cooperative rod body 458 is connected to the reel lifting / lowering spool 256a of the reel lifting / lowering manual hydraulic valve 256. That is, by turning the cutting posture lever 45 about the left and right rotation fulcrum shaft 443 and tilting the cutting posture lever 45 in the left and right direction of the machine body, the left and right rotation frame 444 rotates about the left and right rotation fulcrum shaft 443. The reel raising / lowering linkage rod body 458 is moved up and down, the reel raising / lowering spool 256a is operated, the reel raising / lowering manual hydraulic valve 256 is switched, the reel raising / lowering hydraulic cylinder 251 is operated, and the take-up reel 14 is moved up and down. It is configured to make it.

Meanwhile, the grain discharge link 459 is fixed to the base end portion 47a of the grain discharge lever 47. The upper end side of the plate-shaped conveyor lifting / lowering cooperation rod body 460 is connected to the grain discharge link 459. The lower end side of the conveyor lifting / lowering cooperation rod body 460 is connected to the auger lifting / lowering spool 257a of the auger lifting / lowering manual hydraulic valve 257. That is, by turning the grain discharge lever 47 around the axis of the base end 47a and tilting the grain discharge lever 47 in the front-rear direction of the machine body, the grain discharge link 459 is turned and is used for lifting the conveyor. The associated rod body 460 is moved up and down to operate the auger lifting and lowering spool 257a, to switch the auger lifting and lowering manual hydraulic valve 257 and to operate the auger lifting and lowering hydraulic cylinder 252 and Is configured to move up and down.

The manual lifting / lowering manual hydraulic valve 255, the reel lifting / lowering manual hydraulic valve 256, and the auger lifting / lowering manual hydraulic valve 257 are formed in a harvesting hydraulic valve unit body 258 structure with a single hydraulic valve block, It is attached to the upper surface of the valve support 461 provided on the step floor 5 b of the cab 5. The valve support 461 is disposed at the bottom of the front column 41a. The accelerator lever 46 is connected to an engine rotation control mechanism attached to the engine 7 via an accelerator wire 462.

As shown in FIGS. 1, 7, and 9 to 11, a reaping device 3, a threshing device 9 having a handling cylinder 21, and a traveling machine body 1 having a crawler belt 2 as left and right traveling units are provided. In the combine that supplies the threshing device 9 to the threshing device 9, the left and right traveling speed change levers 43 and 44 are provided on the side column 41b in the vicinity of the driver seat 42, and the side column frame that forms part of the side column 41b Left and right traveling speed change levers 43 and 44 and neutral detent ball mechanisms 417 and 418 as neutral maintaining mechanisms for supporting the left and right traveling speed change levers 43 and 44 at the traveling speed neutral position are disposed on the upper frame 281a. Therefore, the left and right traveling speed change levers 43 and 44 are arranged close to each other, and the operator can easily operate each lever 43 and 44 with one hand. The left and right traveling speed change levers 43 and 44 are supported at the zero travel speed position by the neutral detent ball mechanisms 417 and 418, so that the operator clearly recognizes the forward and backward operation of the left and right traveling speed change levers 43 and 44. While the vehicle speed can be changed by appropriately shifting the left and right traveling speed change levers 43, 44, the operator operates one or both of the left and right traveling speed change levers 43, 44 with one hand. Further, the steering operation for changing the course (moving direction) of the traveling machine body 1 can be easily performed. It is possible to improve the maneuverability in the harvesting operation performed continuously for a long time.

As shown in FIGS. 7 and 9 to 11, left and right neutral detent ball mechanisms 417 and 418 that respectively support the left and right traveling speed change levers 43 and 44 independently of the traveling speed neutral position are provided. The left and right traveling speed change levers 43 and 44 and the left and right neutral detent ball mechanisms 417 and 418 are disposed on both sides of the upper frame 281a with the upper frame 281a extending toward the left side. Therefore, the left and right neutral detent ball mechanisms 417 and 418 can be installed with high precision so as to face the left and right travel shift levers. 44 can be prevented from being supported at an inappropriate position. For example, in a structure in which left and right traveling hydraulic pumps 65 for driving the left and right crawler belts 2 are provided and the outputs of the left and right traveling hydraulic pumps 65 are switched by the left and right traveling shift levers 43 and 44, respectively, Is supported at the neutral position for traveling, the outputs of the left and right traveling hydraulic pumps 65 are maintained at zero, and either or both of the left and right crawler belts 2 can be prevented from being driven. Further, the left and right traveling speed change levers 43 and 44 and the left and right neutral detent ball mechanisms 417 and 418 can be installed at low cost and in a compact manner by utilizing the highly rigid upper frame 281a.

As shown in FIGS. 9 to 11, an interlocking detent ball mechanism 414 as interlocking means for detachably connecting the left and right traveling speed change levers 43 and 44 is provided. The shift levers 43 and 44 are integrally engaged to perform switching operation, and the interlocking detent ball mechanism 414 is detached with a certain operating force or more so that the left and right travel shift levers 43 and 44 can be operated independently. Yes. Accordingly, a shifting operation (an operation for changing the vehicle speed while moving straight) and an operation of either the left or right traveling speed change lever 43, 44 are performed by operating one of the left and right traveling speed change levers 43, 44. Gear shifting operation (steering operation for changing the course while changing the vehicle speed) can be easily executed by one or both of the left and right traveling shift levers 43 and 44 being operated by one operator. . For example, when the left and right traveling speed change levers 43 and 44 can be operated with a certain operating force or less, that is, in a situation where the traveling load is small, the other lever 43, 44 is operated by operating one of the left and right traveling speed change levers 43, 44. 44 can also be switched in conjunction with each other to improve straightness in high-speed movement. On the other hand, when the left and right traveling speed change levers 43, 44 are operated with a certain operating force or more, that is, under a heavy traveling load, either of the left and right crawler belts 2 is controlled by independent operation of the left and right traveling speed change levers 43, 44. The left and right crawler belts 2 can be controlled in response to either or both sideslip or slip, and the reaping device 3 can be moved along an uncut grain culm row, etc. Remaining can be reduced. It is possible to improve harvesting workability such as wet fields that easily slip or slip.

As shown in FIGS. 8 to 12, the brake mechanism 297 for braking the crawler belt 2 and the brake pedal 38 as a brake operating tool for braking the brake mechanism 297 are provided. The left and right traveling speed change levers 43 and 44 are configured to return to the support positions of the neutral maintaining mechanisms 417 and 418. Therefore, the left and right crawler belts 2 can be braked by setting the travel shift to neutral (travel drive output is zero) only by the braking operation of the brake pedal 38. For example, in the structure in which the left and right crawler belts 2 are driven by the traveling hydraulic pump 65 or the traveling hydraulic motor 69, the timing of returning the left and right traveling shift levers 43 and 44 to the neutral position and the timing of braking the left and right crawler belts 2 The traveling hydraulic pump 65 or the traveling hydraulic motor 69 can be prevented from being overloaded, and the crawler 2 driving hydraulic structure incorporating the traveling hydraulic pump 65 or the traveling hydraulic motor 69 or the operation of stopping the left and right crawler tracks 2 can be simplified. Can be That is, while the manufacturing cost of the hydraulic structure for driving the crawler belt 2 can be easily reduced, handling operability such as maintenance of the hydraulic structure for driving the crawler belt 2 can be improved. Further, an emergency stop can be performed by omitting the neutral return operation of the left and right traveling speed change levers 43 and 44, and the slippage of the crawler belt 2 or the excavation of a farm scene can be reduced.

As shown in FIGS. 3, 7, and 14, the structure includes a grain tank 6 that collects grains of the threshing device 9 and a grain discharge conveyor 8 that discharges the grains in the grain tank 6 to the outside of the machine. As the harvesting operation lever, a harvesting posture lever 45 that moves up and down the harvesting device and a grain discharge lever 47 that moves up and down the grain discharge conveyor 8 are provided, and a single unit installed in the steering column 41 in front of the driver seat 42. The base portion of the cutting posture lever 4 and the base portion of the grain discharge lever 47 are supported by a lever fulcrum frame 442 as one lever support. Therefore, the support structure of the cutting posture lever 45 and the grain discharge lever 47 can be easily configured by the lever fulcrum frame 442. With the lever fulcrum frame 442 supporting the cutting posture lever 45 and the grain discharge lever 47, the cutting posture lever 45 and the grain discharge lever 47 can be assembled in the steering column 41. The attaching / detaching workability of the cutting posture lever 45 and the grain discharging lever 47 can be improved.

As shown in FIGS. 13 and 14, a harvesting hydraulic valve unit body 258 is installed in the steering column 41 in front of the driver seat 42, and a cutting lift manual hydraulic valve 255 that is switched by operating a cutting posture lever 45, and a cutting posture lever. A manual hydraulic valve 256 for raising and lowering the reel that is switched by 45 operation and a manual hydraulic valve for raising and lowering the auger (manual hydraulic valve for discharge conveyor) 257 that is switched by operating the grain discharge lever 47 are provided in the hydraulic valve unit body 258 for harvesting work. Yes. Therefore, the hydraulic valves 255, 256, 257 for harvesting work can be concentrated in the steering column 41. A manual hydraulic valve 255 for lifting and lowering, a manual hydraulic valve for lifting and lowering a reel 256, and a manual hydraulic valve for lifting and lowering an auger 257 can be easily connected to the harvesting posture lever 45 and the grain discharge lever 47. Assembling or disassembling of the manual lifting / lowering manual hydraulic valve 255, the lifting / lowering manual hydraulic valve 256, the auger lifting / lowering manual hydraulic valve 257, etc. can be simplified. Maintenance workability of the auger lifting manual hydraulic valve 257 and the like can be improved.

Next, with reference to FIG. 4, FIG. 7, and FIG. 15 to FIG. As shown in FIGS. 15 to 16, using the rear vertical frame 511 and the rear horizontal frame 512 of the cab 5, the mowing clutch lever 39 is provided on the upper left side of the cab 5 (the rear end side of the side column 41 b). And a threshing clutch lever 40 is attached. Lever fulcrum plate 513 erected on the upper surface of the rear horizontal frame 512, lever fulcrum shaft 514 provided on the base end side (lower end side) of the lever fulcrum plate 513, and lever rising stopper provided on the upper end side of the lever fulcrum plate 513 515 and a lever fall stopper 516 that is fixed to the front side of the rear lateral frame 512.

Then, the base end portion of the cutting clutch lever 39 and the base end portion of the threshing clutch lever 40, the base end portion of the cutting lever link 517, and the threshing lever link 518 are pivotally supported on the lever fulcrum shaft 514. A cutting lever link 517 is integrally fixed to the base end portion of the cutting clutch lever 39. A threshing lever link 518 is integrally fixed to a base end portion of the threshing clutch lever 40. Further, a cutting clutch wire 520 is connected to the cutting lever link 517 via a cutting clutch fulcrum crossing link 519.

That is, the cutting clutch lever 39 that is in contact with the lever standing stopper 515 and supported in the standing posture is rotated around the lever fulcrum shaft 514, and the cutting clutch lever 39 is tilted forward of the machine body, The cutting clutch lever 39 is moved to the lying posture to be brought into contact, the cutting clutch wire 520 is pulled via the cutting clutch fulcrum crossing link 519, the cutting clutch 242 is engaged, the cutting drive belt 241 is tensioned, and the cutting device 3 Is configured to operate. Note that the cutting clutch lever 242 is turned off and the cutting device 3 is stopped by returning the lying cutting clutch lever 39 to the standing posture.

On the other hand, as shown in FIGS. 15 to 16, a regulation plate 523 that is fixed to the threshing clutch lever 40 is provided. The restriction plate body 523 is extended on the front side of the cutting clutch lever 39 supported in the standing posture, and the restriction plate body 523 is brought into contact with the front surface of the cutting clutch lever 39 in the standing posture. In the state where the threshing clutch lever 40 is brought into contact with the lever standing stopper 515 and supported in the standing posture, the cutting plate lever 523 is maintained in the standing posture by the restriction plate 523. That is, it is configured such that the forward tilting operation of the cutting clutch lever 39 is blocked by the restriction plate 523. When the threshing clutch lever 40 is supported in the lying posture in contact with the lever lying stopper 516, the cutting clutch lever 39 can be tilted forward.

Further, as shown in FIGS. 15 to 16, a link support frame 526 is provided which is fixed to a connecting portion between the rear end portion of the upper frame 281a and the rear vertical frame 511. A conversion link mechanism 525 is connected to the threshing lever link 518 via a threshing clutch fulcrum crossing link 524. The conversion link mechanism 525 includes a first conversion link 527, a second conversion link 528, and a third conversion link 529. The base end of the first conversion link 527 and the base end of the second conversion link 528 are pivotally supported on a link support shaft 530 provided on the link support frame 526. The base end portion of the first conversion link 527 and the base end portion of the second conversion link 528 are integrally fixed. The tip side of the 1st conversion link 527 is connected with the threshing clutch fulcrum crossing link 524 so that bending is possible.

On the other hand, one end side of the third conversion link 529 is connected to the distal end side of the second conversion link 528 so that it can be bent. Further, the front end side of the threshing clutch rod body 531 is connected to the other end side of the third conversion link 529 via the shaft body 529a. A slide body 532 is fixed to the other end side of the third conversion link 529. The slide body 532 is slidably brought into contact with the slide rail surface 526a formed on the link support frame 526. A spring receiver 533 is fixed to the upper surface of the rear horizontal frame 512, and a lever erecting spring 534 is connected between the threshing lever link 518 and the spring receiver 533.

That is, the threshing clutch lever 40 is brought into contact with the lever standing stopper 515 together with the cutting clutch lever 39 and supported in the standing posture by the pulling force of the lever standing spring 534. The threshing clutch lever 40 in an upright position abutted against the lever standing stopper 515 is rotated around the lever fulcrum shaft 514 so that the threshing clutch lever 40 is tilted forward of the machine body and brought into contact with the lever falling stopper 516. By moving the threshing clutch lever 40, the first conversion link 527 and the second conversion link 528 of the conversion link mechanism 525 are rotated via the threshing clutch fulcrum crossing link 524, and slide through the third conversion link 529. The body 532 is slid forward on the slide rail surface 526a to pull the threshing clutch rod body 531.

Further, as shown in FIGS. 1, 4, 5, 6, and 17, the traveling drive input shaft is parallel to the output shaft 67 of the engine 7 mounted on the traveling machine body 1 below the rear of the Glen tank 6 and at the same height position. 64 is provided. An engine output pulley 483 on the output shaft 67 and an engine output transmission pulley 480 on the travel drive input shaft 64 are connected by an engine output belt 231. The pump case 66 provided with the traveling drive input shaft 64 is fixed to the upper surface side of the traveling machine body 1 through the front support body 271 and the rear support body 272. Left and right traveling hydraulic pumps 65 are built in the pump case 66. Further, a threshing output transmission pulley 481 and a grain discharge drive pulley 482 are provided on the travel drive input shaft 64.

4 and 17, an engine room frame 541 is erected on the upper surface of the rear support 272. A handling cylinder drive case 71 is provided in the engine room frame 541. A threshing input shaft 72 is pivotally supported on the barrel driving case 71. A threshing input pulley 484 on the large diameter side is pivotally supported on one end side of the threshing input shaft 72, and a threshing drive belt 232 is suspended between the threshing output transmission pulley 481 and the threshing input pulley 484 on the large diameter side. A threshing input pulley 485 on the small diameter side is pivotally supported on the other end side of the threshing input shaft 72, and a handling cylinder driving belt 234 is provided between the handling cylinder input pulley 486 on the handling cylinder shaft 20 and the threshing input pulley 485 on the small diameter side. Suspend. Further, a grain discharge pulley 487 is pivotally supported on the rear end side of the bottom feed conveyor shaft 103, and a grain discharge belt 244 is suspended between the grain discharge drive pulley 482 and the grain discharge pulley 487.

As shown in FIG. 17, an arm fulcrum shaft 542 is pivotally supported on the rear support 272 so as to be rotatable. A tension arm 543 is provided on one end side of the arm fulcrum shaft 542 protruding rearward from the rear support 272. The tension roller 233 is rotatably supported on the tension arm 543. In addition, a threshing operation arm 544 is provided on the other end side of the arm fulcrum shaft 542 protruding forward from the rear support 272. A fulcrum bracket body 545 is provided on the engine room frame 541, a threshing operation link body 546 is pivotally supported on the fulcrum bracket body 545, and a tension spring body that can be expanded and contracted on one operation link 546a of the threshing operation link body 546. Through 547, the threshing operation arm 544 is connected. The rear end side of the threshing clutch rod body 531 is connected to the other operation link 546b of the threshing operation link body 546.

That is, by tilting the threshing clutch lever 40 forward and pulling the threshing clutch rod body 531, the tension arm 543 is rotated via the threshing operation link body 546 and the threshing operation arm 544, and the threshing drive is performed. The tension roller 233 is pressure-bonded to the belt 232, and the threshing drive belt 232 is tensioned by the tension roller 233 so that the threshing clutch 9 is activated by entering the threshing clutch. In addition, by returning the threshing clutch lever 40 in the lying posture to the standing posture, the tension of the threshing driving belt 232 by the tension roller 233 is released, the threshing clutch is turned off, and the threshing device 9 is stopped.

Further, as shown in FIGS. 4, 8, and 17, left and right traveling hydraulic motors 69 provided in reduction gear cases 63 as left and right deceleration cases, and left and right traveling hydraulic pumps 65 respectively driving left and right traveling hydraulic motors 69. And a pump case 66 as a counter case in which the left and right traveling hydraulic pumps 65 are provided. The left and right traveling hydraulic pumps 65 are arranged on one end side of the traveling drive input shaft 64 on the traveling drive input shaft 64 as a counter shaft provided in the pump case 66, while the traveling drive input shaft 64 extends in the axial direction. A part 272a of the rear support 272 for installing the pump case 66 is extended, and a bearing holder 268 is provided on the extended end 272a of the rear support 272. The flat surface of the bearing holder 268 is bolted to the flat surface of the extended end portion 272a of the rear support 272 so that the position of the bearing holder 268 can be adjusted in the vertical and horizontal directions. The other end side of the travel drive input shaft 64 is rotatably supported by the bearing of the bearing holder 268. A belt presser 269 of the threshing drive belt 232 is detachably fastened to the bearing holder 268. Therefore, the support strength of the travel drive input shaft 64 can be ensured by the rigidity of the rear support 272. When the threshing drive belt 232 is replaced, by removing the bearing holder 268, the belt presser 269 is also removed, so that the maintainability of the threshing drive belt 232 can be improved.

As shown in FIGS. 7, 15, and 16, a threshing clutch lever 40 as a work clutch lever is provided in the steering column 41 on one side rear side of the driver seat 42, and a tension roller 233 (threshing clutch installed at the rear part of the traveling machine body 1 is provided. ) The mechanism is connected to the threshing clutch lever 40 at the front of the traveling machine body 1, and the threshing clutch lever 40 is connected to the tension roller 233 mechanism by the threshing clutch rod body (connection rod) 531. Therefore, the tension roller 233 mechanism can be a belt tension roller 233 that is inexpensive and easy to maintain. By pushing and pulling the threshing clutch rod body 531 of the threshing clutch lever 40, the high tension belt tension roller 233 necessary for high torque input of the threshing device 9 can be switched to the threshing clutch entering position or the cutting position appropriately. . A connecting structure between the threshing clutch lever 40 at the front part of the traveling machine body 1 and the tension roller 233 mechanism at the rear part of the traveling machine body 1 can be configured at low cost. The manufacturing cost of the tension roller 233 mechanism and the operation structure can be reduced. Handling operability such as assembly / disassembly or maintenance of the tension roller 233 mechanism and operation structure can be improved.

4, 8, and 17, left and right traveling hydraulic motors 69 provided in the left and right reduction gear cases 63, left and right traveling hydraulic pumps 65 respectively driving the left and right traveling hydraulic motors 69, and left and right traveling hydraulic pressures. A pump case 66 is provided as a counter case provided with a pump 65, and left and right traveling hydraulic pumps 65 are arranged on one end side of the counter shaft on a traveling drive input shaft 64 as a counter shaft provided in the pump case 66. On the other hand, a part of the rear support 272 for installing the pump case 66 is extended in the axial direction of the traveling drive input shaft 64, and a bearing holder 268 is provided on the extended end 272a of the rear support 272, Since the bearing holder 268 is configured to support the other end of the travel drive input shaft 64, the travel drive input shaft 64 is highly rigid. The bearing holder 268 can be simply adjusted while the engine output transmission pulley 480 or the threshing output transmission pulley 481 as a power transmission pulley can be assembled to the travel drive input shaft 64 at a low cost. Thus, the traveling drive input shaft 64 can be supported with high accuracy. By providing the belt holder 268 with the belt presser 269 and the like, the structure for attaching the belt presser 269 can be simplified, and maintenance workability such as replacement of the threshing drive belt 232 as a power transmission belt can be improved.

Next, with reference to FIG. 19, the deformation structure of the attachment part of the threshing clutch lever 40 is demonstrated. In place of the threshing clutch rod body 531 and the slide body 532 shown in FIGS. 15 to 17 (first embodiment), a threshing clutch wire 536 and a bearing roller 537 are provided in FIG. 19 (modified structure). As shown in FIG. 19, a threshing clutch wire 536 is stretched through an outer receiver 538 provided on a link support frame 526, and one end side of the inner wire 536a of the threshing clutch wire 536 is connected to the shaft body 529a. The other end side of the inner wire 536a is connected to the operation link 546b. That is, the operation link 546 b is connected to the third conversion link 529 by the threshing clutch wire 536.

Further, a bearing roller 537 is rotatably provided on the shaft body 529a, and the bearing roller 537 is brought into contact with the slide rail surface 526a of the link support frame 526 so as to be freely rotatable. 19, when the threshing clutch lever 40 is raised, the second conversion link 528 and the third conversion link 529 are bent, the inner wire 536a of the threshing clutch wire 536 is loosened, and the tension roller ( (Threshing clutch) 233 is supported at the cutting position. On the other hand, as shown by the phantom line in FIG. 19, when the threshing clutch lever 40 is tilted forward, the second conversion link 528 and the third conversion link 529 extend and the bearing roller 537 faces the front of the body. Since it rolls, the inner wire 536a of the threshing clutch wire 536 is tensioned and the tension roller (threshing clutch) 233 is supported at the entering position.

As a result, due to the boosting action of the toggle mechanism constituted by the second conversion link 528, the third conversion link 529, and the bearing roller 537, for example, half of the tensile force of the tension spring body 547, as in the first embodiment. With the following operation force, the threshing clutch lever 40 is turned on and operated, the threshing drive belt 232 is tensioned, and the power of the engine 7 can be transmitted to each part of the threshing device 9. In addition, when the threshing clutch lever 40 is operated to be engaged, the threshing clutch lever 40 is supported in the engaged position by the action of the lever standing spring 534 exceeding the fulcrum. In addition, although the toggle mechanism comprised by the 2nd conversion link 528, the 3rd conversion link 529, and the bearing roller 537 was arrange | positioned in the body front part which is the vicinity of the threshing clutch lever 4, tension roller (threshing clutch) 233 installation Needless to say, it may be arranged at the rear of the airframe in the vicinity of the part.

As shown in FIG. 15 to FIG. 17 and FIG. 19, a ripening device 3, a threshing device 9 having a handling cylinder 21, a grain tank 6 for collecting grain, and a traveling machine body 1 having a crawler belt 2 as a traveling portion are provided. In the combine that supplies the cereal to the threshing device 9 from the reaping device 3, the engine 7 mounted on the traveling machine 1, the tension roller 233 as a threshing clutch that transmits power from the engine 7 to the threshing device 9, and the tension roller Threshing clutch lever 40 as a working clutch lever for turning on and off 233, and by turning on and off the threshing clutch lever 40, the tension roller 233 is turned on and off via the slide body 532 or the bearing roller 537 as the clutch operating body. It is a structure, and it is a slide body 532 or a bearing roller in the traveling body 1 It is configured to be movably supported in a straight line 37. Therefore, even if a large operating force is required for the on / off operation of the tension roller 233, the operating force of the threshing clutch lever 40 can be easily reduced, and the tension roller 233 can be securely turned on and off, The assembly structure of the bearing roller 537 can be simplified, and the manual operation mechanism of the tension roller 233 can be configured at low cost and in a compact manner.

As shown in FIGS. 15 to 17 and 19, a link support frame 526 is provided as a rail body that supports the slide body 532 or the bearing roller 537 so as to be linearly movable, and the threshing clutch lever 40 is provided with a first link mechanism. The slide body 532 or the bearing roller 537 is connected via the second conversion link 528 and the third conversion link 529, and the slide body 532 or the bearing roller 537 is reciprocated by the guide of the link support frame 526 so that the tension roller 233 is turned on and off. It is configured as possible. Therefore, the slide body 532 or the bearing roller 537 can be displaced in one direction and the tension roller 233 can be turned on and off. For example, the slide body 532 or the bearing roller 537 can be easily incorporated into the support portion of the threshing clutch lever 40, The slide body 532 or the bearing roller 537 can be easily connected to the tension roller 233 by a long steel rod (threshing clutch rod body 531) or the like. Cost reduction or durability improvement of the manual operation mechanism of the tension roller 233 can be achieved.

As shown in FIGS. 15 to 17 and 19, the rear vertical frame 511 as a machine frame standing on the upper surface of the traveling machine body 1 is supported by the threshing device 9 or the Glen tank 6. Further, the threshing clutch lever 40 and the slide body 532 or the bearing roller 537 are arranged so that the operating direction of the threshing clutch lever 40 and the moving direction of the slide body 532 or the bearing roller 537 are matched. Therefore, the support rigidity of the slide body 532 or the bearing roller 537 can be easily ensured by using the highly rigid rear vertical frame 511. The connecting structure of the threshing clutch lever 40 and the slide body 532 or the bearing roller 537 has a simple link mechanism (second conversion link 528, third conversion link 529) and rod (threshing clutch rod body 531) or wire (threshing clutch wire 536). ) And the like. The slide body 532 or the bearing roller 537 can be assembled in a compact manner by utilizing the gap between the threshing device 9 and the Glen tank 6.

As shown in FIGS. 15 to 17 and 19, the threshing clutch lever 40 provided at the front portion of the traveling machine body 1, the engine 7 provided at the rear part of the traveling machine body 1, and the tension for transmitting power from the engine 7 to the threshing device 9. A roller-type threshing clutch (tension roller 233) and a slide rail surface 526a of a link support frame 526 as a guide means for movably supporting the slide body 532 or the bearing roller 537, and facing the longitudinal direction of the traveling machine body 1 Thus, the slide body 532 or the bearing roller 537 is configured to move and be guided linearly. Therefore, the front side of the traveling machine body 1 is connected via a rod (threshing clutch rod body 531) or a wire (threshing clutch wire 536) that extends using the space on the left side surface of the grain tank 6 or the right side surface of the threshing device 9. The tension roller 233 at the rear of the traveling machine body 1 can be easily connected to the threshing clutch lever 40. A threshing clutch lever 40 and a tension roller 233 are arranged in the vicinity of a straight line in the front-rear direction of the traveling machine body 1, and a slide body 532 or a bearing roller 537 and a link support are provided at either the front part of the traveling machine body 1 or the rear part of the traveling machine body 1. The slide rail surface 526a of the frame 526 can be easily assembled.

Next, with reference to FIGS. 9 to 11 and FIGS. 20 to 25, the check structure of the left and right speed change levers 43 and 44 will be described. As shown in FIG. 9 to FIG. 11 and FIG. 20 to FIG. The boss portion 432 of the check arm body 431 is integrally fixed to the right speed change lever 44. A forward check arm 433 that restricts the forward shift operation of the left shift lever 43 and a reverse check arm 434 that restricts the reverse shift operation of the left shift lever 43 are formed integrally with the check arm body 431. As shown in FIG. 20, when the right speed change lever 44 is supported at the neutral position 44a at which the rotational speed of the drive sprocket 51 becomes substantially zero, the forward intermediate speed from the forward slow speed position 43b across the neutral position 43a. Forward operation of the left shift lever 43 that switches steplessly through the position 43c to the forward maximum speed position 43d, and left shift that switches steplessly from the reverse slow speed position 43e to the reverse middle speed position 43f to the reverse maximum speed position 43g. The lever 43 can be operated backward.

As shown in FIG. 20, when the left speed change lever 43 is supported at the neutral position 43a where the rotational speed of the drive sprocket 51 is substantially zero, the forward movement from the forward slow speed position 44b is performed across the neutral position 44a. Forward operation of the right speed change lever 44 steplessly switching to the forward maximum speed position 44d through the medium speed position 44c, and stepless switching rightward from the reverse slow speed position 44e to the reverse maximum speed position 44g via the reverse intermediate speed position 44f The shift lever 44 can be operated backward.

As shown in FIGS. 21 and 22, when the right speed change lever 44 is supported at the forward maximum speed position 44d where the rotational speed of the drive sprocket 51 is the maximum, the neutral position 43a is sandwiched between A shift operation (left turn operation) of the left shift lever 43 that is steplessly switched from a reverse slow speed position 43e to a forward maximum speed position 43d is possible. On the other hand, when the right speed change lever 44 is supported at the reverse maximum speed position 44g at which the rotational speed of the drive sprocket 51 reaches the maximum rotational speed, the forward slow speed position 43b to the reverse maximum speed position across the neutral position 43a. The speed change operation of the left speed change lever 43 which is steplessly switched to 43g is possible. That is, while the crawler belt 2 on the inner side of the turn is driven at the slow forward speed (or the forward speed), the crawler belt 2 on the outer side of the turn is driven at the highest forward speed (or the highest speed at the reverse speed). The operation changes the direction of the traveling machine body 1 so that it can be moved to the start position of the harvesting work for the next stroke.

As shown in FIG. 23, when the left speed change lever 43 is supported at the forward maximum speed position 43d (or the reverse maximum speed position 43g) at which the rotational speed of the drive sprocket 51 is the maximum, the neutral position. The right shift lever 44 can be shifted (right-turning operation) steplessly switched from the reverse slow speed position 44e to the forward maximum speed position 44d (or the forward slow speed position 44b to the reverse maximum speed position 44g) across 44a. It is composed.

As shown in FIG. 22 and FIG. 23, the left and right shifts are performed so that the crawler belt 2 inside the turn rotates backward (or forward) in the reverse direction at a slow speed with respect to the forward rotation (or reverse rotation) of the crawler belt 2 outside the turn. When the levers 43 and 44 are turned, that is, when the crawler 2 outside the turn is driven to rotate in the traveling direction and the crawler 2 inside the turn is driven reversely to change the direction of the steering body 1, the harvesting work in the dry field In this case, the turning radius of the traveling machine body 1 is larger than that of the side-clutch turning structure in which the crawler belt 2 inside the turning is always driven in a reverse state with respect to the traveling direction of the traveling machine body 1 and the power is cut off from the crawler belt 2 inside the turning. Can be reduced, and the disturbance of the field headland can be reduced.

Further, in the harvesting operation in the wet field, during the change of direction, when the shift lever 43 (or 44) inside the turning with respect to the traveling direction of the traveling machine body 1 is switched to the neutral position 43a (or 44a), the crawler belt 2 inside the turning is changed. The drive is stopped, the soil removal action of the crawler belt 2 inside the turn is reduced, and the amount of subsidence of the crawler belt 2 that sinks into the mud of the wetland can be reduced. The traveling body 1 can be smoothly turned toward the vehicle.

Further, as shown in FIG. 24, when the right speed change lever 44 is supported at the forward intermediate speed position 44c at which the rotational speed of the drive sprocket 51 becomes the medium speed rotational speed, the vehicle is moving backward with the neutral position 43a interposed therebetween. A shift operation (left spin turn operation) of the left shift lever 43 that is steplessly switched from the speed position 43f to the forward maximum speed position 43d is possible. When the left speed change lever 43 is supported at the forward middle speed position 43c, the right speed change lever 43 is switched steplessly from the reverse middle speed position 44f to the forward maximum speed position 44d across the neutral position 44a. A speed change operation (right spin turn operation shown in FIG. 25) can be performed. That is, one of the left and right speed change levers 43 and 44 is switched to the forward middle speed position 43c (or 44c) and the other is switched to the reverse middle speed position 43f (or 44f), so that the left or right spin turn is exceeded. It is configured to be able to turn around.

Further, as shown in FIG. 25, when the right speed change lever 44 is supported at the reverse middle speed position 44f at which the rotational speed of the drive sprocket 51 becomes the medium speed rotation speed, the neutral position 43a is sandwiched and the forward movement is in progress. A speed change operation (right spin turn operation) of the left speed change lever 43 which is steplessly switched from the speed position 43c to the reverse highest speed position 43g is possible. When the left shift lever 43 is supported at the reverse middle speed position 43f, the right shift lever 43 is continuously switched from the forward intermediate speed position 44c to the reverse maximum speed position 44g across the neutral position 44a. A speed change operation (left spin turn operation shown in FIG. 24) is configured to be possible.

Next, with reference to FIG. 26, a first modification of the shift lever check structure will be described. 20 to 25, the check arm body 431 is provided on the right speed change lever 44. However, as shown in FIG. An auxiliary check arm body 436 having the same shape as the arm body 431 is provided. The boss portion 437 of the auxiliary check arm body 436 is integrally fixed to the left shift lever 43. A forward check arm 438 that restricts the forward shift operation of the right shift lever 44 and a reverse check arm 439 that restricts the reverse shift operation of the right shift lever 44 are formed integrally with the auxiliary check arm body 436. . Similar to the check arm body 431, the auxiliary check arm body 436 is configured to restrict the speed change operations of the left and right speed change levers 43 and 44.

With the above-described configuration, one or both of the check arm body 431 and the auxiliary check arm body 436 limit the speed change operation of the left and right speed change levers 43 and 44, and for example, check by the operator of the driver seat 42. By configuring the arm body 431 and the auxiliary check arm body 436 so as to be visible, the check arm body 431 and the auxiliary check arm body 436 can be used as indicators for displaying the respective shift operation ranges of the left and right shift levers 43 and 44. Therefore, excessive shifting operation of the left and right shifting levers 43 and 44 can be prevented in advance, and engine troubles can be reduced.

Next, a second modification of the shift lever check structure will be described with reference to FIGS. FIG. 27 is a control circuit provided with a vehicle speed controller 611 showing a second modification, FIG. 28 is a hydraulic circuit diagram thereof, and FIG. 29 is a flowchart of the vehicle speed control. A vehicle speed controller 611 that controls the driving speed of the left and right crawler belts 2 is provided. The vehicle speed controller 611 is formed by a microcomputer. The shift operation amount of the left shift lever 43 is detected.

As shown in FIG. 27, a potentiometer-type left shift sensor 612 that detects a shift operation amount (shift operation position) of the left shift lever 43 as a shift operation tool, and a shift operation amount of the right shift lever 44 as a shift operation tool. The potentiometer-type right shift sensor 613 for detecting (shift operation position), the potentiometer-type shift pedal sensor 615 for detecting the shift operation amount (shift operation position) of the shift pedal 614 as a shift operation tool, and the operation condition of the combine are switched. The dry rice field mode switch 616, the wet rice field mode switch 617, and the road mode switch 618 are input-connected to the vehicle speed controller 611. The operator of the driver seat 42 manually operates the left shift lever 43 or the right shift lever 44 to switch the left shift sensor 612 or the right shift sensor 613, and depresses the shift pedal 614 to switch the shift pedal sensor 615. It is configured so that the dry field mode switch 616, the wetland mode switch 617, and the road mode switch 618 are switched in accordance with the work situation.

In addition, as shown in FIG. 27, the maximum forward vehicle speed setting device 619 that sets the maximum vehicle speed when the traveling machine body 1 moves forward (straight forward), and the highest reverse vehicle speed that sets the maximum vehicle speed when the traveling machine body 1 moves backward (straight forward). A vehicle speed setter 620, a left turn maximum vehicle speed setter 621 for setting the maximum vehicle speed when the traveling vehicle body 1 is turned left, and a right turn maximum vehicle speed setting for setting the maximum vehicle speed when the vehicle body 1 is turned right 622, a left turn maximum vehicle speed setting device 623 for setting the maximum vehicle speed when the traveling vehicle body 1 is turned to the left, and a right turn maximum vehicle speed setting device 624 for setting the maximum vehicle speed when the traveling device 1 is turned to the right. Are connected to the vehicle speed controller 611. The operator of the driver seat 42 operates the setting devices 619 to 624, respectively, to initially set the maximum vehicle speeds.

Further, as shown in FIG. 28, the left speed change cylinder 631 for adjusting the output by changing the angle of the output adjusting swash plate 65a of the left traveling hydraulic pump 65, and the angle of the output adjusting swash plate 65a of the right traveling hydraulic pump 65 are set. A right speed change cylinder 632 that changes and adjusts output, an electromagnetically switched left speed change hydraulic valve 633 that changes the left speed change cylinder, and an electromagnetic change right speed change hydraulic valve 634 that changes the right speed change cylinder 632 are provided. The charge pump 68 is hydraulically connected to the left transmission cylinder 631 and the right transmission cylinder 632 via a left transmission hydraulic valve 633 and a right transmission hydraulic valve 634. As shown in FIG. 27, a left forward solenoid 635 and a left reverse solenoid 636 for switching the left transmission hydraulic valve 633, and a right forward solenoid 637 and a right reverse solenoid 638 for switching the right transmission hydraulic valve 634 are connected to the vehicle speed controller 611. Yes.

With the above configuration, vehicle speed control is executed as shown in FIG. That is, the switching states of the dry rice field mode switch 616, the wet rice field mode switch 617, and the road mode switch 618 are read. Further, the maximum forward vehicle speed setter 619 value, the reverse maximum vehicle speed setter 620 value, the left turn maximum vehicle speed setter 621 value, the right turn maximum vehicle speed setter 622 value, and the left turn maximum vehicle speed setter 623 value The right turn maximum vehicle speed setter 624 value is read. Further, a left shift sensor 612 value that is a shift operation amount of the left shift lever 43, a right shift sensor 613 value that is a shift operation amount of the right shift lever 44, and a shift pedal sensor that is a shift operation amount of the shift pedal 614. Each 615 value is read. And based on each input, the drive speed of the left crawler belt 2 and the drive speed of the right crawler belt 2 are each calculated.

As described above, the left forward solenoid 635 (left forward actuator) or the left reverse solenoid 636 (left reverse actuator) is controlled on the basis of the calculated drive speed of the left crawler belt 2, and the left shift hydraulic valve 633 is controlled. Switching, operating the left shift cylinder 631 to change the angle of the swash plate 65a for adjusting the output of the left traveling hydraulic pump 65, changing the rotation speed of the left traveling hydraulic motor 69 steplessly, or reverse traveling Also, a feedback operation is performed in which the left speed change hydraulic valve 633 returns to neutral by the angle adjustment operation of the output adjustment swash plate 65a, and the output is proportional to the operation amount of the left forward solenoid 635 or the operation amount of the left reverse solenoid 636. The drive speed of the left crawler belt 2 is changed by changing the angle of the adjustment swash plate 65a and changing the rotational speed of the left traveling hydraulic motor 69. To change the vehicle speed).

On the other hand, based on the calculated driving speed of the right crawler belt 2, the right forward solenoid 637 (right forward side actuator) or the right reverse solenoid 638 (right reverse side actuator) is controlled to switch the right speed change hydraulic valve 634 to the right. The shift cylinder 632 is actuated to change the angle of the output adjustment swash plate 65a of the right traveling hydraulic pump 65, to change the rotation speed of the right traveling hydraulic motor 69 steplessly, or to perform a traveling shift operation that reverses the rotation. Further, the angle adjustment operation of the output adjustment swash plate 65a causes a feedback operation to return the right shift hydraulic valve 634 to neutral, and the output adjustment inclination is proportional to the operation amount of the right forward solenoid 637 or the operation amount of the right reverse solenoid 638. The angle of the plate 65a is changed, the rotational speed of the right traveling hydraulic motor 69 is changed, and the driving speed (vehicle speed) of the right crawler belt 2 is changed. To change.

Therefore, as in the first embodiment shown in FIG. 20, when the value of the right shift sensor 613 is in the neutral position where the rotational speed of the drive sprocket 51 is substantially zero, the forward side operation of the left shift lever 43 is performed. (Reverse operation) can be executed. When there is a value of the left shift sensor 612 at the neutral position 43a where the rotational speed of the drive sprocket 51 becomes substantially zero, the forward operation (reverse operation) of the right shift lever 44 can be executed.

Similarly to the first embodiment shown in FIGS. 21 and 22, when the right speed change sensor 613 value is in the forward highest speed position where the rotational speed of the drive sprocket 51 becomes the maximum rotational speed, the neutral position is set. A shift operation (left turn operation) of the left shift lever 43 can be executed to switch continuously from the reverse slow speed position to the forward maximum speed position across the state. On the other hand, when there is a right shift sensor 613 value in the state of the reverse maximum speed position where the rotational speed of the drive sprocket 51 reaches the maximum number of rotations, the state of the forward slow speed position to the reverse maximum speed position of the neutral position is interposed. The shift operation of the left shift lever 43 can be executed to switch to the above state steplessly. That is, while the crawler belt 2 on the inner side of the turn is driven at a slow forward speed (or a forward speed), the crawler belt 2 on the outer side of the turn is driven at the highest forward speed (or the highest speed at the reverse speed), By the operation, the traveling body 1 can be turned and moved to the start position of the harvesting work for the next stroke.

Similarly to the first embodiment shown in FIG. 23, the left speed change lever 43 is in the forward maximum speed position (or the reverse maximum speed position) where the rotational speed of the drive sprocket 51 reaches the maximum rotational speed. Right shift lever that is steplessly switched between the reverse slow speed position and the forward maximum speed position (or forward slow speed position to the reverse maximum speed position) with the neutral position in between. 44 speed change operations (right turn operation) can be executed. Therefore, when either one of the traveling hydraulic pumps 65 as the left and right transmissions is controlled near the maximum forward output, the traveling hydraulic pump 65 as the other transmission can be output backward within a certain range, Compared with the side-clutch turning structure that cuts power with respect to the crawler belt 2, the turning radius of the traveling machine body 1 can be reduced, and the disturbance of the field headland can be reduced.

Further, as in the first embodiment shown in FIGS. 24 and 25, when the right speed change lever 44 is supported in the forward middle speed position where the rotational speed of the drive sprocket 51 is at the medium speed. A shifting operation (left spin turn operation) of the left shift lever 43 can be executed to switch continuously from the reverse middle speed position state to the forward maximum speed position state with the neutral position state interposed therebetween. When the left shift lever 43 is supported in the forward middle speed position, the right position is switched steplessly from the reverse middle speed position to the forward maximum speed position with the neutral position in between. A speed change operation (right spin turn operation) of the speed change lever 43 can be executed. That is, by switching one of the left and right speed change levers 43 and 44 to the forward middle speed position state and the other to the reverse middle speed position state, it is possible to make a super turn by left or right spin turn.

Similarly to the first embodiment shown in FIGS. 24 and 25, when the right speed change lever 44 is supported in the reverse middle speed position where the rotational speed of the drive sprocket 51 is the medium speed. Then, a shifting operation (right spin turn operation) of the left shift lever 43 can be executed, which is steplessly switched from the forward middle speed position state to the reverse maximum speed position state with the neutral position state interposed therebetween. When the left shifting lever 43 is supported in the reverse middle speed position, the right position is switched steplessly from the forward middle speed position to the reverse maximum speed position across the neutral position. A speed change operation (left spin turn operation) of the speed change lever 43 can be executed.

As shown in FIGS. 1, 9 to 11, and 20 to 25, a traveling machine body 1 on which the engine 7 and the like are mounted, and left and right crawler belts 2 mounted on the traveling machine body 1 are provided, and left and right transmission levers 43, 44 are provided. By the operation, the traveling hydraulic pump 65 as the transmission is controlled to the forward output state or the reverse output state, and the traveling drive output is transmitted from the engine 7 to the left and right crawler belts 2 via the traveling hydraulic pump 65, respectively. In the work vehicle, a check arm body 431 or a vehicle speed controller 611 is provided as a check unit that restricts transmission control of the other shift levers 44 and 43 by controlling the traveling hydraulic pump 65 of either the left or right shift levers 43 and 44. The maximum shift range of the reverse operation of the other shift lever 44, 43 is limited by the forward operation or the reverse operation of one shift lever 43, 44. For example, in a combine equipped with a reaping device 3 for reaping the uncut cereal grains in the field and a threshing device 9 for threshing the grains of the reaped cereal grains, a reciprocating movement in the field When harvesting cereal grains, it is possible to improve the direction change workability in the field headland where the forward / backward switching frequency is high. Further, even if the shift levers 43 and 44 are provided so as to be able to shift to the maximum forward speed or the maximum reverse speed, a sudden increase in traveling load can be easily prevented. Therefore, engine troubles can be reduced and steering performance can be improved.

As shown in FIGS. 9 to 11 and 20 to 25, the structure includes left and right traveling hydraulic pumps 65 that are independently controlled to a forward output state or a reverse output state by operating the left and right shift levers 43 and 44, respectively. Thus, when either one of the left and right traveling hydraulic pumps 65 is controlled to be near the maximum forward output, the other traveling hydraulic pump 65 is configured to be capable of backward output within a certain range. When either one is driven at the maximum forward output (or the maximum reverse output), the other crawler belt 2 can be driven at the reverse output (or forward output) below a predetermined value. That is, the crawler belt 2 outside the turning can be driven at the maximum output while the crawler belt 2 inside the turning is driven in reverse. Mobility according to road surface conditions (dry fields, wet fields, traveling on the road, etc.) can be obtained.

As shown in FIGS. 9 to 11 and 20 to 26, a check arm body 431 is provided as a check means, and the check arm body 431 is connected to one or both of the left and right speed change levers 43 and 44, and one speed change is performed. When the levers 43 and 44 are operated, the operable range of the other speed change levers 44 and 43 is limited by the check arm body 431, while when the other speed change levers 44 and 43 are operated, one speed change lever Since the controllable range of 43 and 44 is limited by the check arm body 431, the check arm body 431 can be compactly assembled to the mounting portions of the left and right speed change levers 43 and 44. The shift operation structure can be simplified and the manufacturing cost can be reduced. For example, in a structure in which the left and right crawler belts 2 are respectively driven by the left and right traveling hydraulic pumps 65 constituting the left and right transmissions, they are provided between the swash plate control portion of the left and right traveling hydraulic pumps 65 and the left and right transmission levers 43 and 44. The shift operation structure can be simplified.

As shown in FIGS. 27 to 29, a vehicle speed controller 611 (vehicle speed control means) is provided as a restraining means. By forward control or reverse control of the vehicle speed controller 611 by one speed change lever 43, 44, the other speed change lever 44, 43 is used. Since the maximum speed change output of the reverse speed control of the vehicle speed controller 611 is limited, the vehicle moves at the maximum forward speed or the maximum reverse speed as in the case where the check arm body 431 is provided as the check means. However, it is possible to easily obtain a mobility according to the road surface conditions (dry fields, wet fields, traveling on the road, etc.) while easily preventing a sudden increase in traveling load.

Next, the details of the combine hydraulic structure and travel drive structure in the first embodiment will be described with reference to FIGS. As shown in FIGS. 33 to 37, the pump case 66 in which the left and right traveling hydraulic pumps 65 are built in includes the engine 7 mounted on the right upper surface of the rear part of the traveling machine body 1 and the threshing mounted on the left upper surface of the traveling machine body 1. It fixes to the upper surface side of the traveling body 1 via the front support body 271 and the rear support body 272 between the right side wall body of the apparatus 9. A U-shaped intermediate portion of the front support body 271 is fastened to the upper surface of the traveling machine body 1 with a bolt 773. The left and right sides of the pump case 66 are fastened with bolts 774 to the U-shaped ends of the front support 271. That is, the front part of the pump case 66 in which the charge pump 68 is disposed is supported by the traveling machine body 1 by the front support body 271.

34 to 36, the bottom surface side of the rear support body 272 is fastened with a bolt 776 to the mounting base 775 on the upper surface side of the traveling machine body 1. The rear surface side of the pump case 66 is fastened to the front surface side of the rear support 272 with bolts 777. A support arm body 272a extends rearward from the rear surface of the rear support body 272, and the lower end side of the rear bearing body 778 is fastened to the rear end portion of the support arm body 272a with a bolt 779.

Also, the rear end side of the travel drive input shaft 64 protrudes rearward from the rear surface of the pump case 66, and the travel drive input shaft 64 is passed through the rear support body 272 and the rear bearing body 778. An engine output transmission pulley 780 that suspends an engine output belt 231 and a threshing output transmission pulley 781 that suspends a threshing drive belt 232 are supported on a travel drive input shaft 64 between the rear support 272 and the rear bearing body 778. To do. A grain discharge drive pulley 782 that suspends the grain discharge belt 244 is pivotally supported at the rear end portion of the traveling drive input shaft 64 protruding rearward from the rear bearing body 778. That is, an engine output transmission pulley 780, a threshing output transmission pulley 781, and a grain discharge driving pulley 782 as a counter pulley are pivotally supported on a traveling drive input shaft 64 as a counter shaft.

Further, an engine output pulley 783 is pivotally supported on the output shaft 67 of the engine 7, and the engine output belt 231 is suspended between the engine output transmission pulley 780 and the engine output pulley 783. A threshing input pulley 784 on the large diameter side is pivotally supported on one end side of the threshing input shaft 72, and a threshing drive belt 232 is suspended between the threshing output transmission pulley 781 and the threshing input pulley 784 on the large diameter side. A threshing input pulley 785 on the small diameter side is pivotally supported on the other end side of the threshing input shaft 72, and a handling cylinder driving belt 234 is disposed between the handling cylinder input pulley 786 on the handling cylinder shaft 20 and the threshing input pulley 785 on the small diameter side. Suspend. Further, a grain discharge pulley 787 is pivotally supported on the rear end side of the bottom feed conveyor shaft 103, and a grain discharge belt 244 is suspended between the grain discharge drive pulley 782 and the grain discharge pulley 787.

With the above configuration, the driving force output from the engine 7 is branched and transmitted by the traveling drive input shaft 64 as a counter shaft. That is, the output of the engine 7 is transmitted from the travel drive input shaft 64 to the left and right travel hydraulic pumps 65. Further, the output of the engine 7 is transmitted from the threshing output transmission pulley 781 on the traveling drive input shaft 64 to the barrel 20 of the threshing device 9 via the threshing driving belt 232 and the barrel driving belt 234. On the other hand, the output of the engine 7 is transmitted from the grain discharge drive pulley 782 on the travel drive input shaft 64 to the grain discharge conveyor 8 via the grain discharge belt 244.

As shown in FIGS. 1, 4, 31, 33, 36, and 37, the engine 7 is mounted on the rear part of the traveling machine body 1, and the threshing device 9 and the glen tank 6 are provided on the traveling machine body 1. 9 is provided with a travel drive input shaft 64 as a counter shaft in parallel with the output shaft 67 of the engine 7 and at the same height position, and an engine output pulley 783 on the output shaft 67; The engine output transmission pulley 780 or the threshing output transmission pulley 781 or the grain discharge drive pulley 782 as the counter pulley on the counter shaft 64 and the threshing input pulley 784 of the threshing device 9 are arranged flush with the rear surface of the traveling machine body 1. Therefore, a threshing drive belt 232 or the like that transmits power from the engine 7 to the threshing device 9 is compactly attached to the rear side of the engine 7 or the rear side of the threshing device 9. It can be assembled in. Further, the engine output transmission pulley 780 on which the output belt 231 of the engine 7 is suspended can be disposed at a position where vibration of the engine 7 is reduced. Further, by opening the rear portion of the traveling machine body 1, replacement or maintenance work of the output belt 231 of the engine 7 or the threshing driving belt 232 of the threshing device 9 can be easily performed from the rear side of the traveling machine body 1. That is, the handling workability can be improved while the power transmission structure of the engine 7 can be simplified.

As shown in FIGS. 4, 31, 33, 36, and 37, the left and right traveling hydraulic pumps 65 and the left and right traveling hydraulic motors 69 are provided, and the left and right traveling hydraulic pumps 65 operate the left and right traveling hydraulic motors 69. In this structure, the left and right crawler belts 2 are driven, and the left and right traveling hydraulic pumps 65 are disposed on the traveling drive input shaft 64. Therefore, the traveling hydraulic pump 65 is disposed in the engine room adjacent to the engine 7. Can be installed compactly. Further, the traveling hydraulic pump 65 can be easily air-cooled by the cooling air of the engine 7. The driving efficiency of the crawler belt 2 can be improved while the hydraulic piping structure of the left and right traveling hydraulic pumps 65 and the left and right traveling hydraulic motors 69 can be simplified.

As shown in FIGS. 4, 31, 33, and 37, the engine 7 is mounted on the traveling machine body 1 below the rear part of the Glen tank 6, and the grain discharge pulley 787 of the Glen tank 6 is mounted on the rear surface of the traveling machine body 1. Since the pulleys 780, 781, and 782 are arranged flush with each other, the rear portion of the traveling machine body 1 is opened so that the grain discharge belt 244 of the grain tank 6 can be replaced or maintained by the rear of the traveling machine body 1. Easy to run from the side. While the power transmission structure to the Glen tank 6 can be simplified, handling workability can be improved.

As shown in FIGS. 4, 8, 32, 33, 36, and 37, the threshing device 9 is provided with a grain sorting mechanism 10, and the handling of the threshing device 9 is supported by the handling cylinder. The threshing input pulley 784 is disposed on one end side of the trunk shaft 20 so that a cutting driving force or a sorting driving force is transmitted from the other end side of the barrel shaft 20 to the harvesting device 3 or the grain sorting mechanism 10. Since it is configured, a transmission path from the engine 7 to the harvesting device 3 or the grain sorting mechanism 10 can be easily configured. Maintenance workability of a drive structure such as the reaping device 3 or the grain sorting mechanism 10 can be improved. In addition, the plurality of input portions of the grain sorting mechanism 10 arranged in order from the high rotation side (Tangxia fan) can be efficiently driven with a simple belt drive structure. For example, the Kara fan 29, the first conveyor mechanism 30, the second conveyor mechanism 31, and the swing sorter 26 are used as a small number of sorting drive belts (sorting input belt 235, swing sorting belt 236, conveyor drive belt 237). Can be operated at an appropriate speed.

38 and 39, the reduction gear case (deceleration case) 63 includes a first housing 791, a second housing 792, and a third housing 793. The first housing 791 is bolted to one end of the second housing 792, the third housing 793 is bolted to the other end of the second housing 792, 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 791 via an oil passage base body 794. A traveling hydraulic motor 69 is hydraulically connected to the traveling hydraulic pump 65 via an oil passage base body 794 and hydraulic piping (not shown). A brake mechanism 297 having a brake braking 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 brake lever 296.

Also, the other end side of the motor shaft 295 is inserted into the first housing 791 and the second housing 792. A reduction intermediate shaft 298 is pivotally supported by the first housing 791, the second housing 792, and the third housing 793. One end side of the reduction intermediate shaft 298 is connected to the other end side of the motor shaft 295 through a first reduction gear group 299 as the reduction gear mechanism 263. The traveling axle 300 is pivotally supported by the second housing 792 and the third housing 793. The traveling axle 300 is projected from the third housing 793, and the drive sprocket 51 is pivotally supported on the projecting end portion of the traveling axle 300. The other end side of the reduction intermediate shaft 298 is connected to the traveling axle 300 via the second reduction gear group 301 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 298 through the first reduction gear group 299, and the second reduction gear group is transmitted. The rotation of the deceleration intermediate shaft 298 is transmitted to the traveling axle 300 through 301, and the crawler belt 2 is driven forward or backward by the drive sprocket 51.

As shown in FIGS. 33, 38 and 39, the left traveling hydraulic motor 69 is diagonally forward and upward with respect to the left traveling axle 300 in the assembled state in which the reduction gear case 63 is fixed to the rear end of the track frame 50. On the other hand, the right traveling hydraulic motor 69 is supported obliquely upward and rearward with respect to the right traveling axle 300. That is, the left and right traveling hydraulic motors 69 are supported at the same height as the non-grounded side of the crawler belt 2 and the left traveling hydraulic motor 69 is displaced forward and supported with respect to the traveling axle 300, so that the traveling axle 300 is supported. On the other hand, the right traveling hydraulic motor 69 is displaced backward and supported.

As a result, as shown in FIG. 38, two sets of left and right reduction gear cases 63 are arranged symmetrically about an axle center line 305 connecting the axis centers of the left and right traveling axles 300. Therefore, even if the sum of the left and right width dimensions L1 of the two sets of left and right reduction gear cases 63 that support the traveling hydraulic motor 69 is larger than the reduction gear case installation interval L2 between the left and right crawler belts 2, the left and right traveling hydraulic motors 69 have the same height. It is attached with the support position shifted back and forth at this position. In that case, the left and right brake brake levers 296 are arranged close to the center of the left and right width of the traveling machine body 1. Moreover, as shown in FIG. 33, two sets of left and right reduction gear cases 63 are supported in a gate shape in a rear view (front view). The interior space formed in the gate shape of the left and right reduction gear cases 63 is configured such that the mud in the field moves and the traveling movement resistance of the crawler belt 2 is reduced.

As shown in FIG. 1 and FIGS. 33 to 39, a reaping device 3, a threshing device 9 having a handling cylinder 21, and a traveling machine body 1 having left and right crawler belts 2 are provided. In the supplied combine, the left and right track frames 50 on which the left and right crawler belts 2 are installed are respectively provided with reduction gear cases 63 as left and right traveling drive cases, and the crawler belts 2 are provided at the output portions of the left and right reduction gear cases 63. The left and right driving hydraulic motors 69 respectively provided at the input portions of the left and right reduction gear cases 63 are respectively supported on the inner side of the left and right crawler belts 2 on the non-grounded side. Since the traveling hydraulic motor 69 can be supported outside the crawler belt 2, the traveling hydraulic motor 69 can be attached / detached or the hydraulic piping work can be simplified. Although the manufacturing cost of the traveling hydraulic motor 69 can be easily reduced and the maintenance workability of the traveling hydraulic motor 69 can be improved, the overall height and front width of the combine body can be configured compactly, and the upper surface of the traveling body 1 can be configured. The supporting height of the threshing device 9 or the grain tank 6 installed on the side can be lowered, and the machine body can be prevented from falling over easily. Moving workability such as going into and out of the field or getting over the shore can be improved.

For example, in the civil engineering machine in which the driver's seat, the engine, and the working unit are integrally pivotable, the non-grounding side of the crawler belt 2 can be configured higher, and therefore the reduction gear case 63 can be supported at a position lower than the non-grounding side of the crawler belt 2. However, in the combine that installs the driver's seat 42 and the engine and the working unit (threshing device 9 and the like) using the entire upper surface side of the traveling machine body 1, it is necessary to install the crawler belt 2 below the traveling machine body 1. When the traveling hydraulic motor 69 is supported at a position lower than the non-grounding side of No. 2, the traveling hydraulic motor 69 is supported close to the field scene. Although there is a problem that a lot of mud in the field adheres to the traveling hydraulic motor 69 or a large amount of cigarette wraps around the traveling hydraulic motor 69, the traveling resistance of the crawler belt 2 tends to increase. Then, it is possible to prevent a large amount of mud in the field from adhering to the traveling hydraulic motor 69, or it is possible to prevent the grass from being wound around the traveling hydraulic motor 69, and the traveling resistance of the crawler belt 2 can be reduced.

33 to 39, the drive sprocket 51 is provided on the outer surface of the lower part of the reduction gear case 63, the traveling hydraulic motor 69 is provided on the inner surface of the upper part of the reduction gear case 63, and two sets of left and right reduction gear cases 63 and the traveling hydraulic motor are provided. 69 is arranged in a gate shape when viewed from the front. For example, even when the crawler belt 2 sinks greatly in mud during harvest work such as in a wet field, the two sets of the reduction gear case 63 and the traveling hydraulic motor 69 It is possible to prevent the mud in the field from being smoothly discharged from the lower space and to increase the running resistance of the crawler belt 2. The soil removal resistance of the crawler belt 2 can be reduced to improve the running performance in the wetland. The ground support height of the traveling hydraulic motor 69 can be increased, and the hydraulic piping structure to the traveling hydraulic motor 69 can be simplified.

As shown in FIGS. 34 to 39, the left and right traveling hydraulic motors 69 are arranged in front-rear symmetrical positions in plan view around the axle center line 305 connecting the axis of the left and right drive sprockets 51. The two sets of left and right traveling hydraulic motors 69 and the reduction gear case 63 are formed in the same structure and can be shared as a drive source for the left and right crawler belts 2. Further, even if the lateral width dimension of the traveling hydraulic motor 63 or the reduction gear case 63 is such that the traveling hydraulic motor 69 protrudes to the opposite side of the center of the machine body, the lateral installation distance of the left and right crawler belts 2 is limited. The two sets of left and right traveling hydraulic motors 69 and the reduction gear case 63 can be easily assembled between the left and right crawler belts 2. For example, the left and right traveling hydraulic motors 69 can be spaced apart from each other even when the distance between the left and right crawler belts 2 is smaller than the left and right width dimensions of the left and right reduction gear cases 63 and the traveling hydraulic motor 69. . Mud can be accumulated between the left and right traveling hydraulic motors 69. Further, it is possible to prevent the grass from being wound between the left and right traveling hydraulic motors 69. Maintenance workability of the traveling hydraulic motor 69 can be improved.

Next, the support structure of the drive sprocket 51 and the traveling axle 300 in the reduction gear case 63 will be described with reference to FIGS. As shown in FIGS. 39 to 42, the traveling axle 300 is rotatably supported by the second housing 792 and the third housing 793 via bearing bearings 711 and 712. One end of the traveling axle 300 is projected from the third housing 793 toward the outside of the machine. A spline portion 714 for fitting the boss portion 713 of the drive sprocket 51 and a screw portion 718 for screwing the nuts 716 and 717 through a washer 715 are provided on one end side (projecting end portion) of the traveling axle 300. The drive sprocket 51 is fastened and fixed to the spline part 714 of the traveling axle 300 with nuts 716 and 717.

39-42, a bearing oil seal 719 for sealing the outside of the bearing bearing 712 is fitted into the opening 718 of the third housing 793 outside the bearing bearing 712. A bearing oil seal 719 is fitted on the bearing seal collar 721 on the traveling axle 300, and the opening 718 of the third housing 793 from which the traveling axle 300 protrudes is closed by the bearing oil seal 719. A boss portion 713 of the drive sprocket 51 is extended to the bearing bearing 712 side, and a bearing seal collar 721 is integrally formed on the boss portion 713. The bearing seal collar 721 is fitted on a portion of the traveling axle 300 that is removed from the spline portion 714 on which the drive sprocket 51 is pivotally supported.

That is, the bearing oil seal 719 and the bearing seal collar 721 are provided on the traveling axle 300, and the boss portion 713 of the drive sprocket 51 is extended in the axial direction of the traveling axle 300 so that the boss portion 713 A bearing seal collar 721 is integrally formed at one end, and a bearing seal collar 721 is formed by a part of the boss portion 713. Further, an anti-roll wheel 722 that protrudes from the side surface of the drive sprocket 51 is provided concentrically with the bearing seal collar 721, and the anti-roll wheel 722 is fitted on the step 723 on the outer peripheral side of the opening 718. 3 It is configured to prevent field grass from entering between the housing 793 and the drive sprocket 51.

39-42, an O-ring-shaped axle oil seal body 724 is fitted between the end of the spline part 714 of the traveling axle 300 and the washer 715. As shown in FIG. In other words, an axle oil seal body 724 is provided between the projecting end of the traveling axle 300 projecting from the reduction gear case 63 (third housing 793) and the drive sprocket 51. Lubricating oil (grease or gear oil) is sealed in a spline portion 714 on which the drive sprocket 51 is pivotally supported in the traveling axle 300 by an axle oil seal body 724. The spline portion 714 is lubricated by the lubricating oil, and the wear of the boss portion 713 or the spline portion 714 is reduced.

As shown in FIGS. 1 and 39 to 42, the traveling machine body 1 on which the reaping device 3, the threshing device 9 and the engine 7 are mounted is provided, and a reduction gear case (reduction case) 63 is installed on the traveling machine body 1. The drive sprocket 51 for the crawler belt 2 is pivotally supported on the traveling axle 300, and the engine 7 is made to project from the reduction gear case 63 in the combine that drives the crawler belt 2 installed on the traveling machine body 1 via the drive sprocket 51. An axle oil seal body 724 is provided between the end of the traveling axle 300 and the drive sprocket 51, and the spline portion 714 on which the drive sprocket 51 is pivotally supported of the traveling axle 300 is lubricated. Therefore, it is possible to easily prevent the mud in the field from entering the spline portion 714, and the wear resistance of the spline portion 714 can be easily improved. Further, in the structure in which the bearing oil seal 719 is provided on the bearing 712 bearing portion on the traveling axle 300 via the bearing seal collar 721, the surface pressure of the bearing side end face of the bearing seal collar 721 is reduced, and the bearing seal collar 721 has the resistance to resistance. Abrasion is improved and traveling axle 300 torque can be easily secured.

39 to 42, the bearing oil seal 719 and the bearing seal collar 721 are provided on the traveling axle 300, and the boss portion 713 of the drive sprocket 51 is extended in the axial direction of the traveling axle 300. Since the bearing seal collar 721 is integrally formed at one side end of the boss portion 713, the number of components of the bearing portion of the drive sprocket 51 can be reduced and the manufacturing cost can be reduced. Assembly workability can be improved.

Further, as shown in FIGS. 39 to 42, since the bearing seal collar 721 is fitted on a portion of the traveling axle 300 that is removed from the spline portion 714 on which the drive sprocket 51 is supported, the drive sprocket 51 is provided. Can be easily reduced, and the load resistance of the drive sprocket 51 can be easily improved.

Next, a first modification of the support structure for the drive sprocket 51 and the traveling axle 300 will be described with reference to FIGS. Instead of the structure of the first embodiment shown in FIGS. 39 to 42 in which the bearing seal collar 721 is integrally formed on the boss portion 713 of the drive sprocket 51, the modification shown in FIGS. Separately, a bearing seal collar body 731 is provided. The bearing seal collar body 731 is fitted on the traveling axle 300. A bearing oil seal 719 is fitted on the bearing seal collar body 731. Then, a bearing oil seal 719 is fitted into the opening 718 of the third housing 793.

As shown in FIGS. 43 to 44, a collar step 732 and a seal step 733 are formed in the inner hole (inner diameter side) of the boss 713 in the drive sprocket 51. A small-diameter portion 735 is integrally formed at one end of the bearing seal collar body 731. When the spline part 714 of the traveling axle 300 is fitted to the boss part 713 of the drive sprocket 51 in a state where the O-ring-shaped oil seal body 734 for the collar is fitted to the outer periphery of the small diameter part 735 of the bearing seal collar body 731. A collar step portion 732 is fitted on the small diameter portion 735 of the bearing seal collar body 731, and between the inner peripheral surface of the seal step portion 733 of the boss portion 713 and the outer peripheral surface of the small diameter portion 735 of the bearing seal collar body 731. Further, the color oil seal body 734 is configured to be pressure-bonded.

With the above configuration, the joint between the boss portion 713 of the drive sprocket 51 and the bearing seal collar body 731 is closed by the collar oil seal body 734. That is, the bearing oil seal 719 and the bearing seal collar body 731 are provided on the traveling axle 300, and the drive sprocket 51 and the bearing seal collar body 731 are formed separately, and between the drive sprocket 51 and the bearing seal collar body 731. The collar oil seal body 734 is provided so as to prevent mud in the field from entering the spline section 714 from between the drive sprocket 51 and the bearing seal collar body 731 (joint portion).

43 to 44, a bearing oil seal 719 and a bearing seal collar body 731 are provided on the traveling axle 300, and the drive sprocket 51 and the bearing seal collar body 731 are formed separately. Since the collar oil seal body 734 is provided between the drive sprocket 51 and the bearing seal collar body 731, mud in the field enters the spline portion 714 from between the drive sprocket 51 and the bearing seal collar body 731. Can be easily prevented, and the wear resistance of the spline portion 714 can be easily improved. Further, the surface pressure on the bearing side end face of the bearing seal collar body 731 can be lowered to improve the wear resistance, and the traveling axle 300 torque can be easily secured.

Next, a second modification of the support structure for the drive sprocket 51 and the traveling axle 300 will be described with reference to FIG. As in FIG. 41, a bearing seal collar 721a is integrally formed on the boss 713 of the drive sprocket 51. 43, the bearing seal collar body 731a is fitted on the traveling axle 300. A bearing oil seal 719 is fitted on the bearing seal collar 721a and the bearing seal collar body 731a. The bearing seal collar 721a and the bearing seal collar body 731a are joined within the seal width of the bearing oil seal 719, and the collar oil seal body 734 is provided at the joint between the bearing seal collar 721a and the bearing seal collar body 731a.

45, the collar oil seal body 734 can prevent muddy water from entering the joint portion between the bearing seal collar 721a and the bearing seal collar body 731a from the outer peripheral side. When the joint portion between the bearing seal collar 721a and the bearing seal collar body 731a is separated from the inner end of the spline portion 714, the lubricating oil in the spline portion 714 leaks from the joint portion between the bearing seal collar 721a and the bearing seal collar body 731a. Can be prevented. Compared with the structure of FIG. 21, the intrusion of muddy water into the spline part 714 or the oil leakage from the spline part 714 can be easily reduced.

Next, the combine traveling machine 1 according to the second embodiment will be described with reference to FIGS. 46 and 47. In the following description, the front-rear direction, the left-right direction, and the up-down direction are defined with the arrow F direction as the forward direction, the arrow R direction as the right direction, and the arrow U direction as the upward direction.

The traveling machine body 1 is configured to drive the combine 100 by the power from the engine 7. The traveling machine body 1 is a crawler-type traveling machine body 1, which includes a traveling frame 811, a pair of left and right reduction gear cases (deceleration cases) 63 and 63, a pair of left and right drive sprockets 51 and 51, a pair of left and right tension rollers 52 and 52, and a plurality of them. Intermediate rollers 54, 54, and track rollers 53, 53, and a pair of left and right crawler belts 2, 2, and the like.

46 and 47, the traveling frame 811 constitutes the skeleton of the traveling machine body 1. The traveling frame 811 includes a pair of front and rear connecting frames 811a and 811a and a pair of left and right crawler belt frames 811b and 811b. The connecting frame 811a is disposed in front and rear of the body frame 802, respectively. The connecting frame 811a is connected to the body frame 802 at the center thereof with its longitudinal direction turned to the left and right. The pair of left and right crawler belt frames 811b and 811b are disposed on the left side and the right side of the body frame 802, respectively. The crawler belt frame 811b is connected to the left end and the right end of the pair of front and rear connection frames 811a with the longitudinal direction facing forward and backward.

The pair of left and right reduction gear cases 63 and 63 support the drive sprocket 51 in a rotatable manner and transmit the power of the engine 7. The left reduction gear case 63 is arranged at the left end of the rear connection frame 811a with the output shaft facing left, and the right reduction gear case 63 has the output shaft rightward at the right end of the rear connection frame 811a. It is arranged toward. The output shafts of the pair of left and right reduction gear cases 63 and 63 are configured to be rotatable by power transmitted from the engine 7. Drive sprockets 51 are connected to the output shafts of the pair of left and right reduction gear cases 63 and 63, respectively. That is, the pair of left and right reduction gear cases 63 are configured to rotatably support the drive sprocket 51 and to transmit the power of the engine 7 to the drive sprocket 51.

The pair of left and right drive sprockets 51 and 51 drive the endless belt 818 (crawler belt 2). The pair of left and right drive sprockets 51 and 51 are connected and fixed to the output shafts of the pair of left and right reduction gear cases 63 and 63, respectively, and are rotatably supported. The pair of left and right drive sprockets 51 and 51 are each wound with an endless belt 818 (described later) engaged therewith. Thus, the pair of left and right drive sprockets 51 are configured to transmit the power from the engine 7 to the endless belt 818 as a driving force at the rear ends of the pair of left and right crawler belt frames 811b.

The pair of left and right tension rollers 52 and 52 apply a predetermined tension to the endless belt 818 (crawler belt 2). The tension rollers 52 and 52 are rotatably supported by the idler forks 815 and 815 provided on the pair of left and right crawler belt frames 811b and 811b, respectively, with the rotation axis as the left and right direction. An endless belt 818 (described later) is wound around the pair of left and right tension rollers 52 and 52, respectively. Here, the idler fork 815 that supports the tension roller 52 is configured to be movable in the front-rear direction and is urged forward by a spring or the like (not shown). That is, the tension roller 52 is configured to be urged forward by the idler fork 815. Accordingly, the pair of left and right tension rollers 52 and 52 are configured to apply a predetermined tension to the endless belt 818 at the front end portions of the pair of left and right crawler belt frames 811b and 811b.

A plurality of intermediate rollers 54 and track rollers 53, 53,... Support and guide the endless belt 818 (crawler belt 2). The intermediate roller 54 is disposed above the pair of left and right crawler belt frames 811b and 811b so that the outer peripheral surface (rolling surface) above the intermediate roller 54 overlaps the passing position (rotation locus) of the endless belt rod 818. Is done. The track rollers 53, 53,... Are below the pair of left and right crawler belt frames 811b, 811b, and the outer peripheral surfaces (rolling surfaces) below the rack rollers 53, 53,. ) To overlap each other.

The intermediate roller 54 and the rack rollers 53, 53,... Are rotatably supported by a pair of left and right crawler belt frames 811b. Then, an endless belt 818 described later is engaged with the intermediate roller 54 and the rack rollers 53, 53,. As a result, the intermediate roller 54 and the rack rollers 53, 53,.. In this embodiment, a single intermediate roller 54 and a plurality of rack rollers 53, 53,... Are not limited to this.

The pair of left and right crawler belts 2 and 2 transmit driving force to the field. The pair of left and right crawler belts 2 and 2 are mainly composed of an endless belt 818 and a plurality of crawler plates 819, 819,. The endless belt 818 is composed of a roller chain and is formed in an annular shape having no end. A plurality of metal footboards 819, 819,... That are grounded to the field are connected to the links 818a, 818a,... Of the roller chain constituting the endless belt 818 by bolts or the like (see FIG. 48). That is, the crawler belt 2 is configured by being disposed on the endless belt 818 so that a plurality of crawler plates 819, 819,.

The pair of left and right crawler belts 2 and 2 are wound between a tension roller 52 in front of the crawler belt frame 811b and a drive sprocket 51 behind the crawler belt frame 811b. In this way, the pair of left and right crawler belts 2 and 2 are configured to be rotatable while being wound around the tension roller 52 and the drive sprocket 51 by the drive force from the drive sprocket 51. The pair of left and right crawler belts 2 and 2 are supported and guided by intermediate rollers 54 and track rollers 53 in the middle. Further, a predetermined tension is applied to the pair of left and right crawler belts 2 by the forward biasing force of the pair of left and right tension rollers 52. Accordingly, the pair of left and right crawler belts 2 and 2 can be properly grounded by being supported and guided by the track roller 53 and the track roller 53, and the driving force can be generated by the urging force of the pair of left and right tension rollers 52. It is possible to suppress the occurrence of sagging even if the signal is transmitted. In the present embodiment, the endless belt 818 is made of a roller chain, and the footwear plate 819 is made of metal. However, the present invention is not limited to this.

As described above, the traveling machine body 1 is configured to be able to transmit the power from the engine 7 to the pair of left and right crawler belts 2 and 2 via the pair of left and right drive sprockets 51 and 51 from the pair of left and right reduction gear cases 63 and 63. The traveling machine body 1 is configured such that the crawler plate 819 is appropriately grounded by supporting and guiding the crawler belt 2 with the tension roller 52, the intermediate roller 54, and the track roller 53. Thereby, the traveling machine body 1 is configured so that the combine 100 can travel while suppressing the sinking of the machine body and the occurrence of slip in the field.

Next, the crawler plate 819 will be described in detail with reference to FIG. 47 and FIG. As shown in FIG. 48, the shoe plate 819 includes a substantially rectangular plate-like member 819a, a bending member 819b, and a rib 819c.

The plate-like member 819a is a main structural member of the crawler plate 819. The plate-like member 819a is connected such that one plate surface is in close contact with the endless belt 818 with the long side portion thereof in the left-right direction. The other plate surface of the crawler plate 819 is formed with a plurality of protrusions for improving the frictional force with the field as a ground contact surface.

The bending members 819b and 819b prevent the footwear plate 819 from sinking into the field. The plate-like member 819a is fixed to both left and right ends by welding or the like. The anti-fixed side of the bending members 819b and 819b (the left and right outer sides in the crawler plate 819) is bent with the height from the field to the tip of the bending members 819b and 819b as the bending height H toward the inside of the rotation track of the crawler belt 2. The That is, the crawler plate 819 is configured such that the bending members 819b and 819b are separated from the field by the bending height H when the grounding surface is grounded to the field. At this time, by setting the bending height H between about 20 mm and about 35 mm, it is possible to obtain a crawler plate 819 having a shape suitable for traveling in wet fields and dry fields. Ribs 819c and 819c are fixed to the left and right sides of the plate-like member 819a by welding or the like across the plate-like member 819a and the bending member 819b for reinforcement.

47, the crawler belt 2 constituted by connecting a plurality of such crawler plates 819 is wound around a drive sprocket 51. As shown in FIG. Since the drive sprocket 51 is rotatably supported by the reduction gear case 63, a part of the reduction gear case 63 is disposed inside the rotation track of the crawler belt 2. Accordingly, one bending member 819 b of the crawler plate 819 constituting the crawler belt 2 passes in the vicinity of the reduction gear case 63. That is, the crawler plate 819 is configured such that one bending member 819b is close to the reduction gear case 63 when passing over the upper portion of the reduction gear case 63.

Next, the mode at the time of the driving | running | working in the agricultural field of the combine 100 which concerns on 2nd Embodiment is demonstrated using FIG.

When the combine 100 travels straight in the field, the driving force of the traveling machine body 1 is transmitted to the field via a plurality of crawler plates 819 constituting the crawler belt 2. At this time, since the plurality of crawler plates 819 are simultaneously grounded to the field, the ground contact area between the field and the crawler belt 2 can be increased. Therefore, even in a soft field, the combine 100 can reliably transmit the driving force from the driving force of the traveling machine body 1 without sinking into the field.

When the combine 100 turns in the field, the crawler belt 2 of the traveling machine 1 turns while skidding in the left-right direction. At this time, the crawler belt 2 slides sideways so as to ride on the mud in the field by bending members 819b and 819b fixed to both ends of the crawler plate 819. That is, since the crawler plate 819 has a boat bottom shape when viewed from the front, it is possible to prevent the crawler belt 2 from sinking into the field 2 by preventing the crawler plate 819 from slipping into mud in the field when sliding sideways. Also, even if mud in the field attached to the crawler plate 819 is lifted as the crawler belt 2 rotates and adheres to the upper portion of the reduction gear case 63, one bending member of the crawler plate 819 that passes near the upper portion of the reduction gear case 63 It can be paid off by 819b.

As described above, in the combine 100 that is the agricultural machine having the crawler belt 2 configured by fixing the plurality of crawler plates 819 to the endless belt 818, the bending members 819 b and 819 b that are both ends of the crawler plate 819 are attached to the crawler belt 2. It is bent toward the inside of the rotation trajectory. With such a configuration, even if the crawler belt 2 slides in the left-right direction of the machine body with respect to the field to turn the farm work machine, the bending members 819b and 819b of the crawler plate 819 do not get caught in the mud in the field. Accordingly, the crawler belt 2 can be prevented from sinking into the field, and the turning performance can be improved.

In addition, a reduction gear case 63 that transmits power to the crawler belt 2 is disposed inside the rotation track of the crawler belt 2, and a bending member 819 b that is one end portion of the crawler plate 819 passes through the vicinity of the reduction gear case 63. It is. By configuring in this way, the mud adhering to the upper part of the reduction gear case 63 is wiped off by the bending member 819b which is one end of the crawler plate 819. Therefore, mud can be prevented from accumulating on the upper part of the reduction gear case 63.

Next, the combine 100 of 3rd Embodiment is demonstrated using FIGS. 50-52. Below, only a different point from the combine 100 which concerns on 2nd Embodiment is demonstrated, the same code | symbol is attached | subjected to the member of the structure substantially the same as the combine 100 of 2nd Embodiment, and description is abbreviate | omitted.

As shown in FIGS. 50 and 51, the pair of left and right crawler belts 902 and 902 transmit driving force to the field. The pair of left and right crawler belts 902 mainly includes an endless belt 818 and a plurality of crawler plates 919, 919,. The endless belt 818 is composed of a roller chain and is formed in an annular shape having no end. A plurality of metal crawler plates 919, 919, which are grounded to the field are connected to the links 818a, 818a,... Of the roller chain constituting the endless belt 818 by bolts or the like (see FIG. 52). That is, the pair of left and right crawler belts 902 are configured to be disposed on the endless belt 818 so that a plurality of crawler plates 919, 919,. In the present embodiment, the endless belt 818 is composed of a roller chain and the crawler plate 919 is made of metal, but is not limited thereto.

Next, the crawler plate 919 will be specifically described with reference to FIG.

As shown in FIG. 52, the shoe plate 919 includes a substantially rectangular plate-like member 919a, a bending member 919b, and a rib 919c.

The plate-like member 919a is a main structural member of the crawler plate 919. The plate-like member 919a is connected such that one plate surface is in close contact with the endless band 818 with the long side portion thereof in the left-right direction. On the other plate surface of the crawler plate 919, a plurality of protrusions for improving the frictional force with the field are formed as a ground contact surface.

The bending members 919b and 919b prevent the footwear 919 from sinking into the field. The plate-like member 919a is fixed to both left and right ends by welding or the like. The anti-fixed side of the bending members 919b and 919b (the left and right outer sides of the crawler plate 919) is bent with the height from the field to the tip of the bending members 919b and 919b as the bending height H toward the inside of the rotation track of the crawler belt 902. The That is, the crawler plate 919 is configured such that the bending members 919b and 919b are separated from the field by the bending height H when the grounding surface is grounded to the field (see FIG. 49). At this time, by setting the bending height H between about 20 mm and about 35 mm, it is possible to obtain a crawler plate 919 having a shape suitable for traveling in wet fields and dry fields.

Furthermore, the bending member 919b fixed to the right side of the crawler plate 919 is formed in a trapezoidal shape whose width becomes narrower toward the right side. Similarly, the bending member 919b fixed to the left side of the crawler plate 919 is formed in a trapezoidal shape whose width becomes narrower toward the left side. That is, the crawler plate 919 is configured such that the distance d between the adjacent bending members 919b increases toward both ends. For reinforcement, ribs 919c and 919c are fixed to the left and right sides of the plate member 919a by welding or the like across the plate member 919a and the bending member 919b for reinforcement.

Next, an aspect of the crawler belt 902 wound around the drive sprocket 951 (or the tension roller 52) of the combine 100 according to the third embodiment will be described with reference to FIG.

As shown in FIG. 53A, when engaged with a drive sprocket 951 having a diameter D of the drive sprocket 51 (or tension roller 52) reduced to a diameter D1, the crawler belt 902 wound around the drive sprocket 951 The curvature of the part increases. Therefore, as the diameter D1 of the drive sprocket 951 decreases, the bending members 919b of the adjacent crawler plates 919 approach each other in the portion of the crawler belt 902 wound around the drive sprocket 951. However, since the distance d1 between the bending members 919b and 919b of the adjacent shoe plates 919 is configured to be large in advance, interference between the adjacent shoe plates 919 can be prevented.

As another example of the crawler belt 902, as shown in FIG. 53 (b), the bending length L (see FIG. 52) of the bending members 919b and 919b of the crawler plate 919 is set to a longer bending length L1 in the endless belt 818. When connecting the crawler plates 919, the adjacent bending members 919b of the crawler plates 919 are close to each other in the crawler belt 902 wound around the drive sprocket 51 (or the tension roller 52). However, the bending member 919b has a narrower width at the end of the bending member 919b as the bending length L1 is increased. Accordingly, since the distance d2 between the bending members 919b of the adjacent shoe plates 919 is configured to be large, interference between the adjacent shoe plates 919 can be prevented.

As described above, the bending members 919b and 919b of the footwear plate 919 are formed in a trapezoidal shape whose width becomes narrower toward the ends of the respective bending members 919b.

With this configuration, when the crawler belt 902 goes around the drive sprocket 51 or the like that is a wheel, adjacent crawler plates 919 do not interfere with each other. Therefore, it can be used for an agricultural working machine having a small diameter D such as the drive sprocket 51, or the bending length L of the crawler plate 919 can be increased.

1 traveling machine body 2 crawler track 7 engine 43 left traveling shift lever 44 right traveling shift lever 65 traveling hydraulic pump (transmission)
431 Check arm body (Check means)
611 Vehicle speed controller (control means, vehicle speed control means)

Claims (8)

1. A traveling machine body including a mowing device, a threshing device, and an engine is installed, a speed reduction case is installed on the traveling body, a drive sprocket for a crawler track is pivotally supported on an axle of the speed reduction case, and the drive sprocket is driven by the engine. Through the combine that drives the crawler belt mounted on the traveling machine body,
   An axle oil seal body is provided between the axle end projecting from the deceleration case and the drive sprocket, and the spline portion on which the drive sprocket is pivotally supported of the axle is lubricated. A featured combine.
2. A bearing oil seal and a bearing seal collar are provided on the axle, wherein a boss portion of the drive sprocket extends in the axial direction of the axle, and the bearing seal collar is provided at one end of the boss portion. The combine according to claim 1, which is integrally formed.
3. The combine according to claim 2, wherein the bearing seal collar is fitted on a portion of the axle that is disengaged from a spline portion on which the drive sprocket is pivotally supported.
4. A bearing oil seal and a bearing seal collar body are provided on the axle, and the drive sprocket and the bearing seal collar body are separately formed, and a collar is provided between the drive sprocket and the bearing seal collar body. 2. The combine according to claim 1, wherein an oil seal body is provided.
5. By controlling the transmission to a forward output state or a reverse output state by operating the left and right shift levers, the driving drive output is transmitted from the engine to the left and right crawler tracks via the transmission, respectively.
   There is a check means for restricting the transmission control of the other transmission lever by the transmission control of one of the left and right transmission levers, and the reverse direction of the other transmission lever by the forward operation or the reverse operation of the one transmission lever. The combine according to claim 1, wherein the maximum speed range of operation is limited.
6. The structure includes left and right transmissions that are independently controlled to a forward output state or a reverse output state by operating the left and right shift levers, and one of the left and right transmissions is controlled near the maximum forward output. The combine according to claim 5, wherein the combiner is configured to be capable of reverse output within a certain range from the other transmission.
7. A check arm body is provided as the check means, and when the one shift lever is operated by connecting the check arm body to one or both of the left and right shift levers, there is an operable range of the other shift lever. While being limited by the check arm body, the operable range of the one shift lever is limited by the check arm body when the other shift lever is operated. The combine according to claim 5.
8. Vehicle speed control means is provided as the check means, and the maximum shift output of the reverse control of the vehicle speed control means by the other shift lever is limited by forward control or reverse control of the vehicle speed control means by the one shift lever. The combine according to claim 5, which is configured.

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