JP2013188185A - Transmission for harvester and harvester using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To downsize the whole vehicle body by devising an arrangement structure of shafts in a transmission case, downsizing the transmission case and devising a relative position of the transmission case and a feeder.SOLUTION: A transmission for a harvester is equipped with an input shaft 31 along the right and left direction at one end side in the cross direction at the upper part side of a transmission case 30, and an output shaft 20 along the right and left direction at the other end side at the lower part side of the transmission case 30. Transmission shafts 34 and 35 in a power transmission system from the input shaft 31 to the output shaft 20 are arranged at a lower side than a virtual line segment connecting the axial center p1 of the input shaft 31 to the axial center p2 of the output shaft 20 and along a vertical direction close to one end side of the transmission case 30 and along a horizontal direction close to a bottom side of the transmission case 30.

Description

  The present invention relates to a transmission for a harvester including a transmission case in which each transmission shaft in a power transmission system from an input shaft to an output shaft is disposed, and a harvester using the transmission.

As described above, the transmission for a harvester including the transmission case in which each transmission shaft in the power transmission system from the input shaft to the output shaft is disposed and the harvester using the transmission are described in [1] below. Things are known.
[1] A threshing device whose handling cylinder rotation axis extends in the left-right direction of the vehicle body is disposed near the front part of the vehicle body in the vicinity of the upper part of the front wheel, a motor is disposed in the rear part of the vehicle body, and the transmission between the left and right front wheels And a harvester configured to drive the front wheels. (See Patent Document 1).

Japanese Unexamined Patent Publication No. 09-107773 (paragraph [0007] FIGS. 1 and 2)

  Although the transmission having the structure described in Patent Document 1 and the harvesting machine using the transmission are provided with a transmission near the front portion of the vehicle body, the input shaft and output in the transmission case of the transmission No specific configuration regarding the shaft arrangement structure and the arrangement of each shaft of the power transmission system is disclosed.

  An object of the present invention is to devise the shaft arrangement structure in the mission case to make the mission case compact, and to devise the relative position between the mission case and the feeder to make the entire vehicle body compact. It is in.

[Solution 1]
The technical means of the present invention taken to solve the above-mentioned problems is that an input shaft extending in the left-right direction is arranged on one end side in the front-rear direction on the upper side of the mission case, and the lower side of the mission case An output shaft extending in the left-right direction is disposed on the other end side opposite to the one end portion in the power transmission system, and each transmission shaft in the power transmission system from the input shaft to the output shaft is connected to the axis of the input shaft and the output shaft. Is disposed below the imaginary line connecting the axis of the transmission case and along the vertical direction near the one end of the mission case and the horizontal direction near the bottom side of the mission case. And

[Operation and effect of invention according to Solution 1]
According to the configuration of the present invention relating to the above solution 1, each transmission shaft in the power transmission system from the input shaft to the output shaft is arranged in the vertical direction near one end in the front-rear direction of the transmission case and the bottom side of the transmission case. Are arranged so as to be located below the imaginary line segment connecting the axis of the input shaft on the upper side and the axis of the output shaft on the lower side. It is easy to make the mission case compact in the front-rear direction and the up-down direction.
That is, the power transmission system from the input shaft to the output shaft is not arranged linearly along the vertical direction or the front-rear direction, but the height difference between the input shaft and the output shaft and the front-rear direction By arranging the transmission case along the vertical direction and the front-rear direction so as to use the difference in position, there is an advantage that the dimensions in the vertical direction and the front-rear direction can be made compact.

[Solution 2]
Another technical means of the present invention taken to solve the above problem is that a planetary gear reduction using a hydrostatic continuously variable transmission and a planetary gear mechanism in a power transmission system from the input shaft to the output shaft. The power input to the hydrostatic continuously variable transmission and the power output from the hydrostatic continuously variable transmission are input to the planetary gear speed reducer, from the planetary gear speed reducer. The output is configured to be transmitted to the lower transmission side.

[Operation and effect of invention according to Solution 2]
According to the configuration of the invention relating to Solution 2, the power before the shift by the hydrostatic continuously variable transmission and the power after the shift by the hydrostatic continuously variable transmission are input to the planetary gear reduction device. Will be.
Therefore, compared to the case where only the power after shifting from the hydrostatic continuously variable transmission having low transmission efficiency compared to the mechanical power transmission structure is input to the planetary gear reduction device, the hydrostatic continuously variable transmission is performed. Since power before shifting with good transmission efficiency is input to the planetary gear reduction device as composite power before being input to the device, there is an advantage that power with high transmission efficiency can be obtained as an output from the planetary gear reduction device. is there.

[Solution 3]
Another technical means of the present invention taken in order to solve the above-mentioned problems is characterized in that an inclined surface is formed on the upper surface of the mission case so that the other end portion is lower than the one end portion.

[Operation and effect of invention according to Solution 3]
According to the configuration of the invention relating to the solving means 3 described above, since an inclined surface is formed on the upper surface of the mission case so that the other end side is lower than the one end portion, the space above the inclined surface is formed above the upper portion of the mission case. It is advantageous in that it can be used as a means for avoiding interference with members disposed in the space, or as a means for compactly configuring the mission case itself. Also, dust accumulation on the upper surface of the mission case can be reduced.

[Solution 4]
Another technical means of the present invention taken to solve the above-mentioned problems is that the storage in the transmission case is located at a position lower than the outer peripheral edge of the gear mounted on each transmission shaft in the output shaft and the power transmission system. An oil supply path strainer for sucking oil and guiding it to hydraulic equipment is provided.

[Operations and effects of invention according to Solution 4]
According to the configuration of the invention relating to the above solution 4, since the strainer is disposed at a position lower than the outer peripheral edge of the gear mounted on each transmission shaft, the stirring is performed by the rotation of the gear mounted on each transmission shaft. It is possible to suck the oil at a low position, which is difficult to be performed, through the strainer.
Therefore, there is an advantage that an increase in the oil temperature of the oil to be aspirated can be easily suppressed by avoiding the suction from the portion where the oil temperature is likely to be increased due to the stirring by the rotation of the gear.

[Solution 5]
Another technical means of the present invention taken in order to solve the above problems is a harvesting machine using a transmission for a harvesting machine shown in any of the above solving means 1 to 4, wherein the transmission is the input. The transmission case is arranged with the output shaft positioned in front of the shaft, and the feeder for feeding and transporting the harvested crop is positioned above the transmission case so as to overlap the transmission case in plan view. It is provided.

[Operation and effect of invention according to Solution 5]
According to the configuration of the invention relating to the above solution 5, the output shaft at the front position is located on the lower lower side, and the input shaft on the rear side is located on the upper side. It is easy to construct a compact with a relatively short transmission distance.
In addition, the feeder is located at the top of the mission case and is arranged so as to overlap the mission case in plan view, so the entire vehicle body is compact without being restricted by the width of the feeder or the mission case in the left-right direction. There is an advantage that it is easy to configure.

[Solution 6]
Another technical means of the present invention taken in order to solve the above problem is that the feeder is laterally spaced from the center position in the left-right direction of the vehicle body within the distance between the left and right wheels of the wheel traveling device in the left-right direction. It is arranged at a position biased to one side.

[Operations and Effects of Invention According to Solution 6]
According to the configuration of the invention relating to the solving means 6 described above, the feeder is disposed at a position deviated laterally from the center position within the width of the left and right wheels in the left-right direction. A space can be formed between the feeder and the wheel on the side opposite to the side where the is biased.
Therefore, there is an advantage that the space can be effectively used as a maintenance space under the mission case or the feeder.

[Solution 7]
Another technical means of the present invention taken in order to solve the above-mentioned problem is that the transmission case is located at a position opposite to the side where the feeder is biased, within a gap width in the left-right direction between the left and right wheels. It is characterized by being arranged.

[Operation and effect of invention according to Solution 7]
According to the configuration of the invention relating to the solution means 7 described above, most of the mission case is not hidden under the feeder, but is biased to the side opposite to the side where the feeder is biased. The space above the mission case at the detached position is opened, and maintenance is facilitated. Further, since the relatively heavy mission case is located on the side opposite to the side where the feeder is biased, it is advantageous in that it is easy to maintain a good left-right balance of the vehicle body.

[Solution 8]
Another technical means of the present invention taken in order to solve the above-mentioned problem is that the operation mechanism from the outside with respect to the power transmission system in the mission case has an end of the mission case opposite to the side where the feeder is biased. It is provided in the part.

[Operation and effect of invention according to Solution 8]
According to the configuration of the invention relating to the above solution 8, since an operation mechanism from the outside is provided at the end of the mission case on the side opposite to the side where the feeder is biased, the presence of the feeder is not obstructed. There is an advantage that it is easy to provide an external operation mechanism for the power transmission system.

[Solution 9]
The other technical means of the present invention taken in order to solve the above-mentioned problem includes a threshing device in which the feeder supplies a harvested crop, and the threshing device is arranged at a position on the side where the feeder is biased. It is characterized by.

[Operations and effects of invention according to Solution 9]
According to the configuration of the invention according to the above solution 9, the threshing device is positioned on the extension of the flow direction of the harvested crop by the feeder, the crop flow becomes linear, and the smooth crop processing is easily performed. There is.

[Solution 10]
Another technical means of the present invention taken in order to solve the above-mentioned problem is that a hook portion for suspension is provided on the upper portion of the mission case, and the mission case can be lifted to the feeder via the hook portion. An engaging portion is provided.

[Operations and Effects of Invention According to Solution 10]
According to the configuration of the invention relating to the above solution 10, the suspension hook portion provided in the transmission case is formed. Therefore, when the transmission is assembled or disassembled for maintenance, the hook portion is By engaging with the feeder, it is possible to suspend and support the mission case using the raising and lowering operation of the feeder.
Therefore, there is an advantage that it is easy to perform maintenance work by suspending the mission case without requiring a dedicated suspending means.

It is a right view of a normal type combine. It is a left view of a normal type combine. It is a whole top view of a normal combine. It is a front view of a normal type combine. It is a top view which shows a vehicle body frame. It is a disassembled perspective view which shows the arrangement | positioning relationship of each apparatus with respect to a vehicle body frame. It is a side view which shows the arrangement | positioning relationship of each apparatus with respect to a vehicle body frame. It is the VIII-VIII sectional view taken on the line in FIG. It is an expanded view which shows the internal structure of a transmission. It is a side view of a transmission. It is an expanded view which shows the internal structure of a transmission. It is a diagram which shows a power transmission system. It is a fragmentary sectional view showing a rear wheel operation mechanism. It is a block diagram which shows a control system. It is explanatory drawing which shows a shift operation mechanism. It is explanatory drawing which shows an operation guide. It is a graph which shows a control characteristic. It is a hydraulic circuit diagram. It is explanatory drawing which shows another embodiment of a Glen tank. It is explanatory drawing which shows another embodiment of a power transmission system.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[Overall structure of the combine]
1 to 3 show the left and right side surfaces and the general plan view of the ordinary combine according to the present invention. As shown in these drawings, the ordinary combine according to the present invention includes a traveling device 2 including a pair of left and right front wheels 2F and 2F and a pair of left and right rear wheels 2R and 2R on the lower side of the body frame 1. .
A driving cabin 15 is provided at the front portion of the body frame 1, a threshing device 4 and a grain tank 5 are provided at the rear side thereof, a waste wall treatment device 16 is provided at the rearmost portion, and a horizontal horizontal axis with respect to the body frame 1. A self-propelled vehicle body is configured with a cutting processing device 17 that moves up and down around x1 at the front.
The engine 8 that transmits driving force to the traveling device 2, the threshing device 4, the reaping processing device 17, and the like has a crankshaft (not shown) along the left-right direction of the vehicle body and the right side of the threshing device 4. Located on the side.

Power transmitted to the front wheels 2F of the traveling device 2 via a drive shaft 20 (corresponding to a first output shaft described later) extended from the transmission 3 mounted on the front portion of the vehicle body frame 1 to the left and right. Through a speed reduction case 21 provided in a state of entering a recessed portion formed on a surface facing the vehicle body inward of the front wheel 2F, and a front axle 2a (corresponding to an axle) supported by the speed reduction case 21 It is configured to be transmitted.
As a result, the front wheel 2F is mounted so that the power of the engine 8 is transmitted via the drive shaft 20 and is driven to rotate around the horizontal horizontal axis x2, and its lateral width L1 and diameter D1 are The non-steering wheel is composed of a tire wheel larger than the rear wheel 2R.

  The rear wheels 2R are provided at the left and right ends of the rear wheel support frame 22 mounted at the rear portion of the vehicle body frame 1 so as to be able to swing left and right around the longitudinal axis z1. The steering wheel is provided with a rear axle 2b (corresponding to an axle) that can be steered, and rotates about a horizontal horizontal axis x3 of the rear axle 2b. The left and right width L2 and diameter D2 of the rear wheel 2R are configured by tire wheels set smaller than the front wheel 2F.

As shown in FIG. 1 to FIG. 3 and FIG. 7, an intake pipe 81 having an air cleaner 80 that sucks and supplies outside air to the engine 8 is a right side portion on the back side of the driving cabin 15 as a boarding driving portion. Is attached.
The exhaust pipe 82 for exhausting the exhaust from the engine 8 is attached to the right lateral side on the back side of the operation cabin 15 on the same side as the side where the intake pipe 81 is disposed, and the exhaust port 82a is connected to the intake pipe 81. The air cleaner 80 is provided near the ceiling of the driving cabin 15 away from the air cleaner 80.

[Body frame]
As shown in FIGS. 4 to 6, the vehicle body frame 1 includes a pair of left and right vertical frames 10A, 10A that are formed in a channel shape with an inward opening and a front end of the vertical frames 10A, 10A. The main frame 10 is formed in a rectangular frame shape in plan view, with a pipe-shaped front horizontal frame 10B connecting the sides and a pipe-shaped rear horizontal frame 10C connecting the rear ends of the vertical frames 10A and 10A. Yes.
Although not shown in the figure, the pair of left and right vertical frames 10A and 10A that are long in the front-rear direction has hydraulic pipes, fuel pipes, conductive harnesses, and the like arranged in the front-rear direction in the internal space of the channel-shaped cross section. is there.

The left and right vertical frames 10A and 10A in the main frame 10 have front support frame portions 10a welded and fixed to the front end sides thereof, and the front horizontal frame 10B connects the front support frame portions 10a to each other. Is provided.
The left and right ends of the front horizontal frame 10B extend laterally outward through the left and right vertical frames 10A, 10A, and the speed reduction case 21 is bolted to the outer end flange. A drive shaft 20 extending from the transmission 3 is introduced into the deceleration case 21, and the power of the engine 8 is transmitted from the front axle 2a to the front wheels 2F via the transmission 3 and the deceleration case 21.
Rear support frame portions 10b are fixed to the rear ends of the left and right vertical frames 10A and 10A by welding, respectively, and the rear horizontal frame 10C is provided so as to connect the rear support frame portions 10b to each other. Thereafter, a rear wheel support frame 22 is mounted on a bracket 10c provided at an intermediate position in the left-right direction of the horizontal frame 10C so as to be swingable up and down around the longitudinal axis z1.

  Further, the left and right front support frame portions 10a are provided at the lower position on the rear side away from the pipe-shaped front horizontal frame 10B connecting the front end sides of the transmission case 3 as will be described later with reference to FIGS. A rectangular pipe-shaped connecting frame 10D is installed so as to connect the left and right front support frame portions 10a through the lower side, and this connecting frame 10D can prevent an obstacle that may come into contact from below. It also serves as a means to protect mission case 3.

  A grid-shaped mounting frame 11 for mounting the threshing device 4 and the engine 8 is provided on the upper side of the main frame 10, and is supported by the grid-shaped mounting frame 11 to support the Glen tank 5. The support leg 12 and the cabin support leg 13 for supporting the operation cabin 15 are provided upright.

The grid-like mounting frame 11 includes horizontal grid frames 11a, 11b, and 11c disposed above the vertical frames 10A and 10A so as to cross the left and right vertical frames 10A and 10A in the main frame 10, and the horizontal grid frame. 11a, 11b, 11c and vertical lattice frames 11d, 11e located on the same plane are configured in a lattice shape.
As shown in FIG. 5, of the pair of left and right vertical lattice frames 11d and 11e, the left vertical lattice frame 11d is located along the outside of the left vertical frame 10A, and the right vertical lattice frame 11e is the left and right vertical lattice frames 11e. It is located between the frames 10A and 10A on the side close to the right vertical frame 10A.
The left and right vertical lattice frames 11d and 11e arranged in this way are positioned below the left and right lateral edges of the threshing device 4 so as to support the threshing device 4 stably.

The grid-like mounting frame 11 is formed such that the right end portions of the horizontal grid frames 11a, 11b, and 11c protrude laterally outward from the vertical frame 10A on the right side, and the horizontal grid frame 11a on the front end side. A mounting seat 11f of the engine 8 is provided on the extended portion protruding laterally outward and the extended portion of the horizontal lattice frame 11b at the intermediate position.
As a result, as shown in phantom lines in FIG. 5, the engine 8 can be supported in a state in which most of the engine 8 protrudes laterally outward from the right vertical frame 10A. At this time, the laterally outer end position of the engine 8 is located at the same position as the laterally outer edge of the front wheel 2F and the laterally outer end of the grid-like mounting frame 11, or slightly closer to the vehicle inner side, That is, they are provided at substantially the same position.

  The horizontal lattice frame 11a on the front end side of the lattice-shaped mounting frame 11 is formed so that its left end also protrudes laterally outward from the left vertical frame 10A, and the vertical frame 10A of the horizontal lattice frame 11a. A ladder-like mounting table 14 is installed over an extended portion that protrudes laterally outward and a bracket 14 a that extends leftward outward from the vertical frame 10 </ b> A.

Extending laterally outward from the vertical frame 10A on the right side and extending toward the laterally outward side of the vertical frame 10A on the right side on the rear side of the horizontal lattice frame 11b at the intermediate position and the extended portion of the horizontal grid frame 11c on the rear end side. The support brackets 12a and 12a are formed in a protruding manner.
The support brackets 12a, 12a, the support legs 12b erected above the support brackets 12a, 12a, and the support legs 12c erected from the brackets 12d on the arc-shaped legs 13d of the cabin support leg 13 described later. A support frame 12e for supporting the glen tank 5 by the vehicle body frame 1 is constituted by the receiving frame 12e supported by the vehicle body. As shown in FIGS. 7 and 8, the vicinity of the upper end of the support leg 12 b on the rear end side of the support leg 12 is connected and fixed to the side wall 4 a of the threshing device 4 via a stay 12 f.

  As shown in FIGS. 6 and 7, the cabin support leg 13 for supporting the operation cabin 15 is provided on the upper surface side of the front support frame portions 10a, 10a provided on the front end sides of the left and right vertical frames 10A, 10A. A plurality of straight legs 13a, 13b, 13c erected on the outer periphery of the front wheel 2F, and an arcuate leg 13d curved in an arc shape from the outer end of the horizontal lattice frame 11a on the outer peripheral rear side of the front wheel 2F toward the upper outer periphery of the front wheel 2F. And the upper ends of the straight legs 13a, 13b, 13c and the arc-shaped legs 13d are connected by a rectangular base frame 13e.

Out of the straight leg 13a, 13b, 13c, the front and rear straight legs 13a, 13c are arranged in a forward leaning position in front of the upper end side, and the intermediate straight leg 13b is arranged in an upright position. By doing so, it is disposed so as to connect the lower end portion of the front straight leg 13a and the upper end portion of the rear straight leg 13c, and as a whole, it has a rigid structure similar to the truss structure. .
The thus constructed cabin support leg 13 is provided symmetrically on the front end side of the left and right vertical frames 10A, 10A, so that the front portion of the driving cabin 15 projects forward from the front end of the main frame 10. It is configured to be supported in a state.

  For the vehicle body frame 1 configured as described above, the driving cabin 15, the threshing device 4, the grain tank 5, the waste straw processing device 16, the engine 8, and the cutting processing device 17 are arranged as follows. Yes.

[Driving cabin]
That is, as shown in FIGS. 1 to 4 and 7, the driving cabin 15 is mounted and installed on the upper side of the cabin support leg 13 and is positioned higher than the upper edge of the outer diameter of the front wheel 2F. Thus, it is disposed so as to be positioned further forward than the rear edge of the front wheel 2F.
Further, in the left-right direction, as shown in FIG. 3 and FIG. 4, a little to the left of the center line CL of the vehicle body in the left-right direction corresponding to the center of the left and right front wheels 2F, 2F (right side of the page in FIG. 4) It is arranged near.

A steering handle 15a for steering operation and the like is provided in the driving cabin 15, and the rear wheel 2R is steered by the operation of the steering handle 15a.
Although not shown in the figure, various operating tools and instruments for maneuvering operations and work operations are provided in the driving cabin 15, and a parking brake pedal and a speed change operating tool, which will be described later, are also provided. .
Further, in the operation cabin 15, a steering angle display monitor 15d as a display indicating the steering direction of the rear wheel 2R, which will be described later, and a weight converted value corresponding to the grain weight stored in the grain tank 5 are provided. A weight display monitor 15e for displaying is also provided.

  In addition, the code | symbol 15b shown in FIG. 4 is a work lamp, and is provided so that the harvesting work location by the cutting processing apparatus 17 may be irradiated from the upper part of the driving | running | working cabin 15. Reference numeral 15 c is a headlamp provided to irradiate the front from the lower part of the driving cabin 15.

[Threshing equipment]
As described above, the threshing device 4 has the left and right lateral sides of the threshing device 4 as shown in FIGS. 5 and 8 with respect to the grid-shaped mounting frame 11 disposed on the main frame 10 of the vehicle body frame 1. The edges are arranged along the left and right vertical lattice frames 11d and 11e. As a result, the threshing device 4 is disposed in a state in which the threshing device 4 is positioned within the interval width between the left and right front wheels 2F and the rear wheel 2R in the left-right direction.
At this time, the front side of the left lateral edge of the threshing device 4 protrudes laterally outward from the vertical frame 10A on the left side of the main frame 10 and is in a state of close proximity to the inner side end of the front wheel 2F in the left-right direction. However, on the rear side, the rear wheel 2R is disposed on the inner side in the left-right direction with respect to the maximum steering range.

In the threshing device 4 arranged in this way, the barrel rotation axis p1 that is the center line in the left-right direction of the entire threshing device 4 is on the left side with respect to the center line CL in the left-right direction of the vehicle body. It is arranged in a biased state. That is, the center line in the left-right direction of the threshing device 4 is present at the same position as the front and rear barrel rotation axis p1 of the barrel 40 disposed inside.
Moreover, since the lower surface of the threshing device 4 is mounted on the grid-shaped mounting frame 11 as described above, as shown in FIGS. 7 and 8, it is more than the front axle 2a of the front wheel 2F that is a non-steering wheel. It is slightly lower and is located slightly higher than the rear axle 2b of the rear wheel 2R that is the steering wheel. That is, the front axle 2a of the front wheel 2F that is a non-steering wheel or the rear axle 2b of the rear wheel 2R that is a steering wheel is disposed at substantially the same height.

  The threshing device 4 itself is a well-known full-throw-in type that includes a handling cylinder 40 having a front and rear handling cylinder rotation axis p <b> 1 at the upper part of an internal handling chamber, and a sorting unit 41 at the lower part thereof. A threshing process is performed on grains such as cereals fed from the harvesting processing device 17 side to the handling chamber via the feeder 17A provided at the front part, and the grain is collected by the sorting unit 41 and sent to the glen tank 5 to be drained. Is configured to be fed into the rear waste straw processing apparatus 16. The code | symbol 42 in FIG. 1 is the threshing part cover which shields the left side part of the threshing apparatus 4 from the position outside the engine 8, and is comprised so that attachment or detachment is possible.

The feeder 17A is disposed in a state of being deviated to the left with respect to the center line CL in the left-right direction of the vehicle body as in the case 40, and as shown in FIG. The transmission 3 that is biased to the right with respect to the line CL is disposed at a position that partially overlaps in plan view.
The waste straw processing device 16 is integrally attached to the rear portion of the threshing device 4, and is configured to cut the waste straw after the threshing treatment and discharge it to the outside.

〔engine〕
As shown in FIG. 5, the engine 8 is provided in an extended portion protruding laterally outward of the horizontal lattice frame 11 a on the front end side of the lattice-shaped mounting frame 11 and an extended portion of the horizontal lattice frame 11 b at an intermediate position. It is disposed on the mounting seat 11f. As a result, the engine 8 is located on the right lateral outer side opposite to the side on which the threshing device 4 is biased, on the rear side of the right front wheel 2F, and laterally outward of the vertical frame 10A on the right side of the support leg 12. Of the front and rear support legs 12b and 12b that are erected from the support brackets 12a and 12a that are formed to protrude toward the front, the front support legs 12b are positioned on the front side.

The laterally outer end position of the engine 8 is provided so as to be substantially the same as the laterally outer edge of the front wheel 2F in the front-rear direction or slightly closer to the inner side of the vehicle body, that is, at substantially the same position.
Further, the engine 8 has an outer end position in the left-right direction that is the same position as the lateral outer end of the grid-like mounting frame 11 that is a part of the body frame 1 or slightly closer to the inward side of the vehicle body. It is provided so as to be positioned, that is, at substantially the same position.

Since the lower surface of the engine 8 is mounted on the grid-shaped mounting frame 11 as described above, as shown in FIGS. 7 and 8, the engine 8 is slightly lower than the front axle 2a of the front wheel 2F which is a non-steering wheel. The rear wheel 2R, which is a steering wheel, is positioned slightly higher than the rear axle 2b. That is, the front axle 2a of the front wheel 2F that is a non-steering wheel or the rear axle 2b of the rear wheel 2R that is a steering wheel is disposed at substantially the same height.
The upper end of the engine is disposed so as to be slightly lower than or equal to the upper end of the outer peripheral edge of the front wheel 2F.

The engine 8 is disposed between the front axle 2a and the rear axle 2b in a side view and on the side close to the front axle 2a. As a result, a space s1 corresponding to the distance between the front and rear support legs 12b, 12b is formed on the rear side of the engine 8, and the engine 8 is maintained from the rear side using this space s1. be able to.
Further, since the laterally outward side of the engine 8 is opened to the outside by removing the threshing portion cover 42, maintenance from the laterally outward side can be easily performed.
Since the upper space s2 exists between the upper side of the engine 8 and the bottom 50 of the Glen tank 5 placed on the upper side of the support leg portion 12, the upper space s2 is used for the upper side. It is also possible to perform maintenance from.

[Glen tank]
As shown in FIGS. 6 to 8, the Glen tank 5 is a front-rear direction in which a right bottom 50 a located on the right side of the threshing device 4 is provided at the upper end of the support leg 12 among the bottom 50 of the Glen tank 5. Of the threshing device 4 is supported by a portion corresponding to the left bottom 50b of the bottom 50 of the Glen tank 5 with respect to the top plate 4b near the left side wall 4a of the threshing device 4. Has been. Thereby, the Glen tank 5 is extended in the state overhanging on both the right and left sides of the threshing device 4.

  The Glen tank 5 swings around a swing axis z2 along the front-rear direction of the right side portion by an expansion / contraction operation of a dump cylinder 29 interposed between the bottom 50 of the Glen tank 5 and the threshing device 4. Is configured to do. By this swinging operation, as shown by the phantom line in FIG. 8, the inclined discharge posture in which the end portion on the side away from the swing axis z2 is raised, and the swinging shaft as shown by the solid line in FIG. The posture can be changed to the storage posture in which the end portion on the side away from the center z2 is lowered and brought close to the horizontal.

  A right lateral side portion of the Glen tank 5 is constituted by an opening / closing lid 51. The opening / closing lid 51 is for opening / closing an opening formed on the lateral side of the grain storage space inside the grain tank 5, and is the same as the swing axis z <b> 2 of the grain tank 5. As shown by the phantom line in FIG. 8, it rotates a predetermined amount around the axis and opens the lateral side of the grain storage space, and the stored crop inside the glen tank 5 flows down under its own weight. It is configured to provide guidance.

  The lateral width of the Glen tank 5 is set to a lateral width that is approximately the same as the lateral width of the vehicle body frame 1, and the center position in the lateral direction substantially coincides with the center line CL of the vehicle body. In addition, the vertical height of the Glen tank 5 is set to be smaller than the lateral width thereof so that the uppermost part of the upper surface of the Glen tank 5 is approximately the same as the upper surface of the ceiling of the operation cabin 15. It is configured.

A pressure sensor 52 is connected to the pressure oil supply path to the dump cylinder 29 as shown in FIG. 18, and the detection information detected by the pressure sensor 52 is input to the control device 100 described later. The control device 100 includes weight display means 104 (see FIG. 14) stored in advance in a nonvolatile memory as a program.
Based on the detection information detected by the pressure sensor 52, the weight display means 104 calculates a weight converted value corresponding to the grain weight stored in the Glen tank 5, and the weight installed in the driving cabin 15. A command for displaying the weight converted value is output to the display monitor 15e (see FIG. 14).
Accordingly, when it is desired to detect the grain weight in the Glen tank 5, the circuit pressure of the pressure oil supply path is detected by operating the dump cylinder 29 slightly upward, and accordingly, the weight display monitor 15e displays the circuit pressure. The grain weight is displayed.

As shown in FIGS. 7 and 8, the Glen tank 5 has a right bottom portion 50 a supported by the support leg portion 12 corresponding to the upper portion of the engine 8 among the bottom portions 50. It is comprised so that it may be located lower than the left side bottom part 50b.
Thereby, as shown in FIG. 8, the right bottom 50a of the Glen tank 5 is in a state of being provided at a height position overlapping with the top plate 4b bulging in the trapezoidal shape of the threshing device 4 in a side view.

At this time, the height of the upper part of the support leg 12 is set so as to overlap the handling cylinder 40 of the threshing device 4 in a side view. The vertical height of the space s1 formed on the lower side of the receiving frame 12e is also considerably increased.
Therefore, when the threshing part cover 42 is removed, the lateral outer side of the side wall 4a of the threshing device 4 is also opened relatively widely, which is convenient when the threshing device 4 is maintained.

[Reaping processing device]
As shown in FIGS. 1 to 3, a cutting processing device 17 that moves up and down around a horizontal horizontal axis x1 on the front side of the threshing device 4 mounted on the vehicle body frame 1 is provided.
The reaping treatment device 17 includes a feeder 17A that supplies crops such as stalks that have been harvested to the threshing device 40, a scraping reel 17B that scrapes crops such as planting stalks, and a reaping device 17C. The crop is harvested, sent to the feeder 17 </ b> A, and supplied to the threshing device 4.
The crop conveyance direction of the feeder 17A is the front-rear direction along the barrel rotation axis p1 of the barrel 40 in the threshing device 4, and the scraping reel 17B and the reaping device 17C are also lifted and lowered with the lifting and lowering operation of the feeder 17A portion. It is configured to be possible.

And this feeder 17A is arrange | positioned with respect to the centerline CL in the left-right direction of a vehicle body in the state biased to the left side same as the side where the threshing device 4 was biased, and as shown in FIG. A space s3 wider than the space between the left side edge of the feeder 17A and the left front wheel 2F is formed between the right side edge of 17A and the inner side surface of the right front wheel 2F.
The wide space s3 is surrounded by the right side edge of the feeder 17A, the inner side surface of the right front wheel 2F, the front cutting process device 17, and the rear transmission case 30, and the front, rear, left and right. The size is set to such a size that an operator can enter the space s3 and perform maintenance work on the transmission 3, the feeder 17A, the cutting processing device 17, and the like. At this time, if the feeder 17A is lifted, a space is also formed on the lower side of the feeder 17A and it is possible to sink into the lower side of the feeder 17A, so that it becomes easier to work.

〔transmission〕
As shown in FIGS. 9 to 11, the transmission 3 is configured by combining a hydrostatic continuously variable transmission 3A, a planetary gear reduction device 3B using a planetary gear mechanism, a gear transmission 3C, a differential device 3D, and the like. It is. Among these devices 3A, 3B, 3C, and 3D, the planetary gear reduction device 3B, the gear transmission 3C, and the differential device 3D are disposed inside the mission case 30, and the left side outside the mission case 30. The hydrostatic continuously variable transmission 3A is attached to the lateral side surface 30a (right side in FIG. 9). In this way, the transmission 3 is configured by incorporating the devices 3A, 3B, 3C, and 3D as transmissions into the transmission case 30.
The transmission case 30 is connected and fixed in a state where it is placed on the upper side of a rectangular pipe-shaped connection frame 10 </ b> D that connects the left and right front support frame portions 10 a provided at the front portion of the main frame 10.

The mission case 30 is formed in a box shape that can be divided into left and right with a division surface F in the vertical direction corresponding to a joint portion between the open ends of the pair of left and right division case bodies 30A and 30B as a boundary.
And in the state joined to the box shape, it has horizontal side surfaces 30a, 30b along the vertical direction on the left and right sides of the bottom surface 30e along the horizontal direction, and the front side surface along the vertical direction on the front side and the rear side, respectively. 30d and a rear side surface 30f, and on the upper side, a part of the rear end side is horizontal, and an upper surface 30c formed on an inclined surface in which the front side is inclined downwardly toward the front end side.
Thus, the mission case 30 is formed in a substantially rectangular shape in a plan view and a substantially triangular box shape in a side view.

Further, as shown in FIG. 5, the mission case 30 is disposed so as to partially overlap the feeder 17 </ b> A of the cutting processing device 17 in a plan view.
The mission case 30 configured as described above is configured so that the lower surface of the feeder 17A does not come into contact with the mission case 30 as shown in FIG. 7 when the feeder 17A is lowered to the lowermost position. 30 is formed such that the inclined portion of the upper surface 30c has substantially the same inclination angle as the inclination of the lower surface of the feeder 17A lowered to the lower limit position.

  In the mission case 30, as shown in FIG. 9 and FIG. 10, the axial direction is aligned in the left-right direction at a location near the rear end, which is one end side in the front-rear direction on the upper side of the mission case 30. An input shaft 31 is provided. A drive shaft 20 (corresponding to a first output shaft) whose axial direction is aligned in the left-right direction at a position near the front end corresponding to the other end opposite to the one end on the lower side of the mission case 30. ) Is arranged.

The transmission shafts 34 and 35 in the power transmission system from the input shaft 31 to the drive shaft 20 are below the imaginary line segment a connecting the axis p1 of the input shaft 31 and the axis p2 of the drive shaft 20. In addition, the transmission case 30 is disposed along the vertical direction near the one end and the horizontal direction near the bottom surface 30e of the transmission case 30.
That is, as shown in FIGS. 9 and 10, the speed change transmission shaft 34 is disposed near the position directly below the input shaft 31, and the branch transmission is transmitted to a position approximately the same as the axis p <b> 2 of the drive shaft 20. A shaft 35 is provided, and an imaginary line segment connecting the input shaft 31, the transmission transmission shaft 34, the branch transmission shaft 35, and the drive shaft 20 is a rear side surface 30f of the transmission case 30 in a side view. The transmission shafts 34 and 35 of the power transmission system are arranged so as to be substantially L-shaped along the bottom surface 30e.

An input pulley 31 a is fixed to the right end portion of the input shaft 31 (left side in the paper of FIG. 9), and the driving force from the engine 8 is transmitted via the transmission belt 83.
The left end of the input shaft 31 (on the right side in FIG. 9) is integrated with the pump shaft 32a of the hydraulic pump 32 in the hydrostatic continuously variable transmission 3A fixed to the left lateral surface 30a of the mission case 30. The engine power is transmitted as a driving force of the hydraulic pump 32.

The motor shaft 33a of the hydraulic motor 33 in the hydrostatic continuously variable transmission 3A is coaxially rotatable with respect to the speed change transmission shaft 34 installed over the left and right lateral surfaces 30a and 30b in the transmission case 30. It is connected.
The motor shaft 33a and the transmission transmission shaft 34 constitute an input shaft and an output shaft of the planetary gear reduction device 3B, and the sun gear 33b of the planetary gear reduction device 3B is configured to rotate integrally with the motor shaft 33a. A carrier 34a for supporting the planetary gear 34b that is mounted and meshed with the outer peripheral side of the sun gear 33b is mounted so as to rotate integrally with the transmission shaft 34.
A planetary gear 34b rotatably supported by the carrier 34a is mounted so as to revolve on the outer peripheral side of the sun gear 33b, and a ring gear 31d that meshes with the outer peripheral side is provided. The ring gear 31d meshes with both the transmission gear 31c of the input shaft 31 and the planetary gear 34b inside and outside so as to transmit the rotation of the input shaft 31 via the transmission gear 31c provided on the input shaft 31. ing.

  The sun gear 33b, the carrier 34a, the planetary gear 34b, and the ring gear 31d constitute a planetary gear reduction device 3B. The power of the motor shaft 33a and the input shaft 31 is input to the planetary gear reduction device 3B. The transmission power is output to the transmission transmission shaft 34 through the carrier 34a.

As the transmission gear 34c, the transmission transmission shaft 34 has three types of transmission gear portions, that is, a high speed gear portion g1, a medium speed gear portion g2, and a low speed gear portion g3, which rotate relative to the transmission transmission shaft 34. A shift operation mechanism that is supported by the bearings and that selectively engages each of the gear portions g1, g2, and g3 and engages the transmission gear shaft 34 so as to rotate integrally therewith. 7 is provided.
The speed change transmission gear 34c, together with the speed change gears 35a, 35b, 35c provided on the branch transmission shaft 35, alternatively transmits the speed change power to any of the gears 35a, 35b, 35c. Thus, a gear transmission 3C for performing a high / low speed change operation is configured.

  The branch transmission shaft 35 is also installed over the left and right lateral surfaces 30a, 30b in the mission case 30. In addition to the high speed gear 35a, the medium speed gear 35b, and the low speed gear 35c, the branch transmission shaft 35 has a non-steering system first gear meshing with the differential gear 36 of the differential device 3D that transmits power to the front wheels 2F. The first transmission gear 35d and the steering-system second transmission gear 35e that meshes with the transmission gear 38a of the relay transmission shaft 38 that transmits power to the rear wheel 2R are provided to rotate integrally.

The transmission gear 34c includes three types of gear portions g1, g2, and g3, which are a high speed gear portion g1, a medium speed gear portion g2, and a low speed gear portion g3, and the branch transmission shaft 35 includes a high speed gear 35a. In addition to the medium-speed gear 35b and the low-speed gear 35c, the non-steering first transmission gear 35d that meshes with the differential gear 36 of the differential 3D that transmits power to the front wheels 2F, and power is transmitted to the rear wheels 2R. The steering transmission second transmission gear 35e meshing with the transmission gear 38a of the relay transmission shaft 38 is provided so as to rotate integrally.
The high speed gear portion g1 of the transmission gear 34c and the high speed gear 35a of the branch transmission shaft 35 are always meshed, and the medium speed gear portion g2 of the transmission gear 34c and the medium speed gear 35b of the branch transmission shaft 35 are connected. Is always meshed, the low speed gear portion g3 of the transmission gear 34c and the low speed gear 35c of the branch transmission shaft 35 are always meshed, and the first transmission gear 35d of the branch transmission shaft 35 is always in contact with the differential gear 36 of the differential device 3D. The second transmission gear 35e of the branch transmission shaft 35 is always meshed with the transmission gear 38a of the relay transmission shaft 38.

  Any one of the gear portions g1, g2, and g3 of the high speed gear portion g1, the medium speed gear portion g2, and the low speed gear portion g3 of the transmission gear 34c is selectively selected by the shift operation mechanism 7. Thus, as will be described later, the power transmitted to the transmission transmission shaft 34 is shifted and transmitted to the branch transmission shaft 35, and the high-speed gear portion g1 in the transmission transmission gear 34c, Three types of shift gear parts, a medium speed gear part g2 and a low speed gear part g3, and a high speed gear 35a, a medium speed gear 35b, and a low speed gear 35c in the branch transmission shaft 35 are provided in the driving cabin 15 (not shown). A sub-transmission device operated by the sub-transmission lever is configured.

  The non-steering driving force input to the differential gear 36 is transmitted to the left and right drive shafts 20 and 20 (corresponding to the first output shaft) via the differential 3D, and the left and right drive shafts 20. 20 is transmitted to the speed reduction mechanism 21a in the speed reduction case 21 of the left and right front wheels 2F. In the speed reduction case 21, the power reduced by the speed reduction mechanism 21a constituted by the planetary gear mechanism is transmitted to the front axle 2a, and the front wheels 2F are driven.

Each of the left and right drive shafts 20 and 20 is provided with a side brake 20a having a plurality of friction plates on the outer peripheral side thereof. The brake 20a is configured to be operated.
The differential device 3D includes a differential lock mechanism 37 that can be switched between a differential lock state and a differential lock release state by inserting / removing a differential lock pin 37a. It is configured to be performed in conjunction with the stepping-in operation and the stepping-off operation accompanying the stepping-in again.

As shown in FIG. 11, the driving force of the steering system input to the relay transmission shaft 38 is an axis perpendicular to the axis of the relay transmission shaft 38 via a bevel gear 38b provided on the relay transmission shaft 38. And is transmitted to a bevel gear 39a of a rear wheel drive shaft 39 (corresponding to a second output shaft) directed rearward.
Of the power branched from the branch transmission shaft 35 via the drive transmission tool 24 connected to the shaft end of the rear wheel drive shaft 39, the steering system driving force is transmitted to the rear wheel via the rear axle 2b. It is configured to be transmitted to 2R.

The lateral side surface 30a on the side where the hydrostatic continuously variable transmission 3A of the transmission case 30 is provided is more than the imaginary line segment a connecting the axis p1 of the input shaft 31 and the axis p2 of the drive shaft 20. A gear pump 25 for supplying pressure oil to various hydraulic actuators is also mounted on the upper side, positioned closer to the input shaft 31 than the drive shaft 20 in the front-rear direction.
The input of driving force to the gear pump 25 is configured such that power is transmitted from the branch gear 31b provided in the middle of the input shaft 31 to the input gear 25b provided at the shaft end of the pump driving shaft 25a of the gear pump 25, It is configured to be driven by the power of the input shaft 31.

  As shown in FIG. 9, the gear pump 25 passes oil stored in the mission case 30 through a strainer 26a provided near the bottom surface 30e of the mission case 30, and an oil supply passage 26 connected to the strainer 26a. It is configured to inhale through. The oil stored in the mission case 30 has a liquid level h at a height where the branch transmission shaft 35 and the drive shaft 20 exist so that the oil can be used as lubricating oil for each gear in the mission case 30. Reserved until it reaches the limit.

  As shown in FIG. 18, the gear pump 25 includes a power steering device 60 for steering the rear wheel 2R, which is a steering wheel, a cutting lift cylinder 27 for lifting and lowering the entire cutting processing device 17, and a cutting processing. It is used to drive a reel lifting cylinder 28 for raising and lowering the scraping reel 17B of the device 17 and a dump cylinder 29 for raising and lowering the glen tank 5, and these power steering device 60, cutting and raising and lowering. The cylinder 27, the reel raising / lowering cylinder 28, and the dump cylinder 29 constitute an actuator driven by the gear pump 25.

  A parking brake 18 having a plurality of friction plates 18a and pressing bodies 18b is attached to a portion of the branch transmission shaft 35 protruding from the right lateral surface of the transmission case 30 to the outside. Although not shown, the pressing body 18b of the parking brake 18 is in a braking state in which the friction plate 18a is pressed by stepping on a parking brake pedal provided in the driving cabin 15 to prevent the branch transmission shaft 35 from rotating. By releasing the depression of the brake pedal, the brake release state in which the pressing of the friction plate 18a is released is established.

Although not shown, the linkage operating mechanism that links the pressing body 18b of the parking brake 18 and the parking brake pedal provided in the driving cabin 15 is along the right lateral surface of the mission case 30 provided with the parking brake 18. It is provided.
That is, the cam 18 (not shown) provided on the rotating cam shaft 18c is rotated by the operation lever 18d provided with the rotating cam shaft 18c that is rotated around the horizontal axis p4. A braking state in which the pressing body 18b can be operated to the pushing side of the friction plate 18a by a pressing action, and the operation lever 18d is rotated to operate the pressing body 18b to the pushing side of the friction plate 18a; The friction plate 18a is configured to be switchable to a brake release state in which the pressing to the pushing side is released.

The rotating cam shaft 18c is urged to swing toward the return side (braking release side), and the parking brake pedal is locked in the driving cabin 15 in the depressed state, whereby the parking brake is operated via the linkage operation mechanism. The parking brake 18 is maintained, and the parking brake pedal 18 is unlocked by releasing the lock of the parking brake pedal via the linkage operation mechanism.
And since the said linkage operation mechanism is provided along the right side surface on the opposite side to the left side surface which overlapped the lower side of the feeder 17A among the side surfaces of the mission case 30, it overlaps with the feeder 17A. Regardless, the operation lever 18d for operating the parking brake 18 and the linkage operation mechanism can be easily maintained from the outside.

  Note that reference numeral 30g shown in FIG. 9 denotes a hook portion that can be used when the mission case 30 is suspended, and can be attached by screwing to a mounting seat 30h provided on the upper surface 30c of the mission case 30. It is configured. By providing an engaging portion (not shown) for the hook portion 30g at the lower portion of the feeder 17A, the operating force of the cutting lift cylinder 27 is utilized during assembly / disassembly when the feeder 17A moves up and down. It is also possible to suspend and support the mission case 30.

[Rear wheel drive system]
A drive transmission shaft 24 (corresponding to a drive transmission tool) connected to the rear wheel drive shaft 39 for transmitting a driving force to the rear wheel 2R is equipped with a threshing device 4 in the vertical direction as shown in FIG. The lower edge of the body frame 1, that is, above the lower edge of the vertical frame 10 </ b> A of the main frame 10, below the lower surface of the threshing device 4, that is, below the upper edge of the grid-like mounting frame 11. It is arranged.
In plan view, as shown in FIG. 5, the threshing device 4 is disposed slightly to the right along the right lateral edge.
Thus, when the maintenance work is performed with the lower surface side of the threshing device 4 opened, it is possible to avoid the drive transmission shaft 24 from interfering with the work. Further, since the drive transmission shaft 24 does not exist below the lower edge of the vehicle body frame 1, it is easy to avoid contact with other objects, and no installation space is required above the vehicle body frame 1, so the vehicle body frame 1 It does not interfere with the equipment placed above.

The power transmission structure from the rear wheel drive shaft 39 to the rear axle 2b is configured as follows.
That is, as shown in FIGS. 5 and 12, the drive transmission shaft 24 is concentrically connected via the shaft joint 24 a on the extension line of the rear wheel drive shaft 39.
The power transmitted to the drive transmission shaft 24 is directed back and forth via a bevel gear 24b provided at the rear end of the drive transmission shaft 24 and a lateral transmission shaft 66 having bevel gears 66a and 66b on the upper and lower transmission sides. It is transmitted to the front end side bevel gear 67 a of the transmission shaft 67.

The front-rear transmission shaft 67 is rotatably supported by the vehicle body frame 1 so as to be positioned coaxially with the front-rear direction axial center z1 of the rear wheel support frame 22, and a rear end side provided on the rear end side. A bevel gear 67 b is located inside the rear wheel support frame 22.
The rear wheel support frame 22 is formed in a box shape having a rectangular cross section, and a rear wheel transmission shaft 68 is provided therein. The input bevel gear 68a provided at the intermediate portion of the rear wheel transmission shaft 68 meshes with the rear end side bevel gear 67b of the front-rear transmission shaft 67, and the output gears 68b and 68b provided at the left and right ends of the rear wheel transmission shaft 68 are left and right. The rear wheel axle 2b is engaged with a transmission gear 69a of an interlocking shaft 69 connected via a universal joint 69b so that a driving force is transmitted to the rear wheel 2R.

  As shown in FIG. 13, the rear axle 2b is rotatably supported by a pair of left and right bearings 2d and 2d with respect to the rear axle case 2c. A seal 2e is interposed between the rear axle 2b and the rear axle case 2c, and a seal cover 2f is mounted on the inner side of the vehicle body. Thus, the seal 2e is prevented from being damaged even when straw scraps or weeds are wound around the rear axle case 2c or a shaft support boss 23 described later.

[Rear wheel operation mechanism]
The rear wheel operating mechanism 6 for operating the rear wheel 2R constituting the steering wheel so that the direction of the rear wheel 2R can be freely changed around the vertical swing axis y1 is configured as shown in FIG. 5 to FIG. 8 and FIG. .
That is, a rear axle 2b (corresponding to an axle) is vertically pivoted on both left and right ends of a rear wheel support frame 22 that is mounted on the rear portion of the vehicle body frame 1 so as to be swingable left and right around the longitudinal axis z1. A pivot tube portion 22a is pivotally supported around the center y1 so as to be rotatable.
A vertical pivot shaft 23a formed integrally with a pivot boss 23 that rotatably supports the rear axle 2b around a horizontal horizontal axis x3 is fitted into the pivot cylinder 22a. The pivot shaft 23a is supported so as to prevent it from coming off downward.
Between the outer peripheral surface of the pivot shaft portion 23a and the inner peripheral surface of the pivot tube portion 22a fitted on the outer peripheral surface, O-rings 22b and 22b are interposed at upper and lower ends thereof, and the outer peripheral surface. Grease is enclosed between the inner peripheral surface and the inner peripheral surface.

The left and right rear wheels 2R, which are steered with the vertical swing axis y1 as the center of swing, have a pitman arm 62 that is in a state of facing forward and inward when traveling straight forward via a tie rod 61. It is connected to the device 60.
As shown in FIG. 14, in the power steering device 60, detection information detected by a steering operation amount detector 64 for detecting a steering operation amount of the steering handle 15a is input to a control device 100 composed of a microcomputer. The piston rod 60b of the power steering device 60 is expanded and contracted to change the steering direction based on the command of the steering operation means 101 stored in advance in the nonvolatile memory of the control device 100 as a program. is there.
The cylinder 60a of the power steering device 60 is fixedly supported by the rear wheel support frame 22 that swings left and right around the longitudinal axis z1 so as to swing right and left around the longitudinal axis z1 together with the rear wheel support frame 22. It is configured.

  A steering angle detector 63 including a rotary encoder that detects a relative angle difference with respect to the pivot shaft portion 23a that is linked to the swing operation of the pitman arm 62 is provided at the upper end portion of the pivot tube portion 22a. . The angle information detected by the steering angle detector 63 is input to the control device 100 composed of a microcomputer, and the command of the steering angle display means 103 stored in advance as a program in the nonvolatile memory of the control device 100 is used. Based on this, the steering angle of the rear wheel 2R is displayed on the steering angle display monitor 15d (see FIG. 14) in the driving cabin 15 as an image or a numerical value.

The drive transmission shaft 24 connected to the rear wheel drive shaft 39 is also provided with a drive speed detector 65 comprising a rotary encoder that detects the rotational speed of the drive transmission shaft 24. The detection information of the driving speed by the driving speed detector 65 is input to the control device 100, and based on the command of the steering speed control means 102 stored in advance in the nonvolatile memory of the control device 100 as a program. The opening degree of the power steering control valve 60c, which is an electromagnetic control valve that controls the operation of the power steering device 60, is adjusted. The higher the driving speed, the lower the operating speed of the power steering device 60 is controlled.
In other words, during high-speed travel where the travel speed of the vehicle body becomes high, the angle change operation of the rear wheel 2R by the power steering device 60 is performed when the same steering operation is performed during low-speed travel even if a relatively rapid steering operation is performed. It is configured so as to be performed at a relatively slow speed as compared with the angle changing operation, and is controlled so as not to perform a sudden turn during high speed traveling.

[Shift operation mechanism]
The shift operation mechanism 7 for performing a speed change operation of the speed change transmission gear 34c is configured as follows.
As shown in FIGS. 10 and 15, the shifters 70 and 71 for shifting the speed change transmission gear 34c of the auxiliary transmission are axially connected to a shift guide shaft 72 parallel to the speed change transmission shaft 34 for supporting the speed change transmission gear 34c. It is slidably mounted.
The shifters 70 and 71 are positioned between the high-speed gear part g1 and the medium-speed gear part g of the transmission gear 34c, so that the high-speed gear part g1 and the medium-speed gear part g are alternatively used. A first shift member 70a for engaging / disengaging the rotational transmission portion 34d of the transmission transmission shaft 34, and a second shift member 71a for engaging / disengaging the low speed gear portion g3 with respect to the rotational transmission portion 34d of the transmission transmission shaft 34. It has.

  A cylindrical shaft portion 70c provided with an arm portion 70b for operating the first shift member 70a along the axial direction of the speed change transmission shaft 34, and an arm portion for operating the second shift member 71a along the axial direction of the speed change transmission shaft 34. A cylindrical shaft portion 71 c having 71 b is fitted on the shift guide shaft 72. Engaging recesses 70d and 71d are formed in these cylindrical shaft portions 70c and 71c, respectively, and shift operation members 75 and 76 are engaged in the engaging recesses 70d and 71d, respectively.

The shift operation members 75 and 76 are respectively supported by two support shafts 73 and 74 disposed in a direction orthogonal to the shift guide shaft 72, and are provided for each shift operation member 75 and 76. The support shafts 73 and 74 are provided so as to be rotatable around the axis.
Concave portions 75b and 76b are formed in the boss portions 75a and 76a of the shift operation members 75 and 76, respectively, and a plurality of steel balls 77 are interposed between the concave portions 75b and 76b. The steel ball 77 is housed in a straight tubular guide hole (not shown) and is configured to be movable only on an imaginary line segment b connecting the axes of the two support shafts 73 and 74.

The length L3 of the six steel balls arranged on the imaginary line segment b on the imaginary line segment b is equal to the bottom surfaces of the recesses 75b and 76b formed in the boss portions 75a and 76a of the shift operation members 75 and 76 on both sides. Are positioned so as to oppose each other (indicated by a solid line in FIG. 15), the distance is shorter than the interval L4 on the imaginary line segment b, and the boss portions 75a and 76a of the shift operation members 75 and 76 on both sides are provided. Is set longer than the interval L5 between the outer peripheral surfaces.
Therefore, if the steel ball 77 is not in the recesses 75b and 76b in either one of the shift operation members 75 and 76, the other shift operation members 75 and 76 can be rotated. Therefore, this serves as a check mechanism that enables operation of one of the shift operation members 75 and 76 and prevents operation of the other shift operation member 75 or 76.

The function of the check mechanism will be described with reference to FIG. 15. As shown by the solid line in FIG. 15, when the steel ball 77 enters the recess 76 b of the second shift member 76, the first shift member 75 is connected to the solid line. From the neutral position shown, the operation can be performed on either side of the position of the high speed gear portion g1 of the transmission gear 34c or the position of the medium speed gear portion g2 of the transmission gear 34c.
However, as indicated by phantom lines in FIG. 15, in the state where the steel ball 77 protrudes from the recess 76b of the second shift member 76, the second shift member 76 is engaged with the low speed gear portion g3 of the transmission gear 34c. In this state, the first shift member 75 cannot be moved from the neutral position indicated by the solid line.
Conversely, the first shift member 75 is moved from the neutral position shown by the solid line to either the position of the high speed gear portion g1 of the transmission gear 34c or the position of the medium speed gear portion g2 of the transmission gear 34c. Since the steel ball 77 is in a state in which the steel ball 77 enters the recess 76b of the second shift member 76 in the state of being operated, the second shift member 76 is engaged with the low-speed gear portion g3. Cannot switch to the state.
As a result, the steel ball 77 enters the concave portion 75b, 76b of either one of the shift operation members 75, 76, that is, one of the shift operation members 75, 76 is operated to the neutral position. If it is not in the state, the other shift operation members 75 and 76 are restrained so that the rotation operation cannot be performed.

[Transmission system]
The power transmission system from the engine 8 to the traveling device 2 is configured as shown in the power system diagram of FIG.
The output from the engine 8 is input to the input shaft 31 of the transmission 3 via the transmission belt 83 and the input pulley 31a.
The power transmitted to the input shaft 31 is transmitted to the hydraulic pump 32 of the hydrostatic continuously variable transmission 3A through a pump shaft 32a that is concentrically connected to the input shaft 31 so as to rotate integrally therewith. ing. The power is branched and transmitted to the gear pump 25 via a branch gear 31b provided on the input shaft 31 and to the ring gear 31d of the planetary gear reduction device 3B via a transmission gear 31c.

  The motive power transmitted to the hydrostatic continuously variable transmission 3A is shifted and output from the motor shaft 33a of the hydraulic motor 33 and input to the sun gear 33b of the planetary gear reduction device 3B. Therefore, the combined force of the power input from both the hydraulic motor 33 side and the input shaft 31 side is transmitted to the carrier 34a of the planetary gear reduction device 3B, and the combined force is used as the shifted power to the carrier 34a. Is transmitted to the speed change transmission shaft 34.

The hydrostatic continuously variable transmission device 3A and the planetary gear reduction device 3B constitute a main transmission device of a traveling drive system, and the main transmission device includes a main transmission lever 45 provided in the driving cabin 15. In the forward / backward swinging operation (see FIG. 16), the speed change from the forward-side maximum speed position (maximum speed position F2 to be described later) to the backward-side position (backward position R to be described later) steplessly along the guide groove of the operation guide G. It is configured so that it can be operated.
The main transmission including the hydrostatic continuously variable transmission 3A and the planetary gear reduction device 3B has output characteristics as shown in the chart of FIG.

That is, the output speed of the main transmission at a predetermined engine speed is as shown in FIG. The horizontal axis in FIG. 17 indicates the swash plate angle of the hydraulic pump 32 operated by the main transmission lever 45, and the vertical axis indicates the vehicle speed.
The medium-speed output line segment La shown in FIG. 17 is in the medium-speed output state of the auxiliary transmission (the state where the medium-speed gear portion g1 of the transmission gear 34c is engaged with the medium-speed gear 35b of the branch transmission shaft 35). The correlation between the swash plate angle and the vehicle speed is shown.
At this time, when the main transmission lever 45 is operated to the maximum work efficiency speed position F0, the swash plate angle of the hydraulic pump 32 is 0 degree and the vehicle speed is about 2 m / s.
That is, the swash plate angle of the hydraulic pump 32 is 0 degree and the hydraulic motor 33 is not driven, but the power from the transmission gear 31c of the input shaft 31 is directly transmitted to the planetary gear reduction device 3B via the ring gear 31d. When the rotation of the carrier 34a based on the rotational speed ratio between the sun gear 33b and the ring gear 31d in the stopped state passes through the speed change transmission shaft 34, the maximum operating speed position on the line La in the medium speed output state of the auxiliary transmission. The output speed is F0.
Therefore, it is useful to carry out the mowing work at the output speed at the work maximum efficiency speed position F0 in order to perform the vehicle running with the highest transmission efficiency by mechanical transmission without any transmission loss due to hydraulic transmission.

In FIG. 17, the output from the hydrostatic continuously variable transmission 3 </ b> A rotates in the forward direction (forward direction) on the right side of the position where the swash plate angle is 0 degrees in the drawing, and the hydrostatic type on the opposite left side. The output from the continuously variable transmission 3A rotates in the reverse direction (reverse side).
Therefore, when the main transmission lever 45 is moved further forward from the work maximum efficiency speed position F0 in the guide groove of the operation guide G as shown in FIG. 16 and operated to the work maximum speed position F1, as shown in FIG. The swash plate angle of the hydraulic pump 32 reaches a position of about 10 degrees, and the vehicle speed is about 3 m / s.
Conversely, when the main speed change lever 45 is moved backward from the maximum work efficiency speed position F0 and the swash plate angle is operated to about 20 degrees in the reverse rotation direction (neutral stop speed position N in FIG. 16), the reverse rotation occurs. The rotation speed ratio between the sun gear 33b in the state and the ring gear 31d that transmits the drive in the forward rotation direction becomes 1: 1, the rotation of the carrier 34a stops, and the vehicle speed becomes 0 m / s.
A low speed movement region G1 in the guide groove of the operation guide G in a range from the neutral stop speed position N to the work maximum speed position F1 is a work speed range used for normal mowing work. The vehicle speed is increased or decreased according to the operation amount of the main transmission lever 45 in the low speed movement region G1.

  When the main speed change lever 45 is further moved forward from the work maximum speed position F1, the high speed movement region G2 suitable for traveling on the road, etc. is operated beyond the work maximum speed position F1. In the high-speed movement region G2, the swash plate angle of the hydraulic pump 32 is tilted forward until the maximum speed position F2 is reached, and the vehicle speed is operated to the acceleration side according to the operation amount of the main transmission lever 45.

When the main transmission lever 45 is operated backward from the neutral stop speed position N so that the swash plate angle exceeds the position of about 20 degrees in the reverse direction, the vehicle body is moved backward beyond the neutral stop speed position N. The reverse movement area G3 is operated.
In the reverse movement region G3, the rotation of the carrier 34a based on the rotation speed ratio between the sun gear 33b in the reverse rotation state and the ring gear 31d that transmits the drive in the normal rotation direction becomes a rotation in a direction that drives the transmission shaft 34 in the reverse rotation direction. This is the driving force to move the vehicle backward. In the reverse movement region G3, the vehicle speed to the reverse side is operated to the acceleration side until the reverse position R is reached in accordance with the operation amount of the main shift lever 45 to the reverse side.

  The power transmitted to the transmission shaft 34 is transmitted to the branch transmission shaft 35 via the transmission gears 34c and the transmission gear 35 (the high speed gear 35a, the medium speed gear 35b, and the low speed gear 35c). It is configured to be transmitted. In this speed change transmission gear 34c, there are three types of shift gear parts, a high speed gear part g1, a medium speed gear part g2, and a low speed gear part g3, and a high speed gear 35a, a medium speed gear 35b, and a low speed gear 35c on the branch transmission shaft 35. Constitutes a sub-transmission device that is operated for shifting by a sub-transmission lever (not shown) provided in the driving cabin 15.

  The medium speed output state La of the sub-transmission device in which the medium speed gear portion g1 of the speed change transmission gear 34c meshes with the medium speed gear 35b of the branch transmission shaft 35 is the medium speed output line segment La. The high-speed output state of the auxiliary transmission in which the high-speed gear portion g2 meshes with the high-speed gear 35a of the branch transmission shaft 35 is a high-speed output line segment that is steeper than the medium-speed output line segment La as shown in FIG. The low-speed output state of the sub-transmission device in which the low-speed gear portion g3 of the transmission gear 34c meshes with the low-speed gear 35c of the branch transmission shaft 35 is Lb, as shown in FIG. This is indicated by a low-speed output line segment Lc that is gentler than La.

The power transmitted to the branch transmission shaft 35 is transmitted to the differential gear 36 that meshes with the first transmission gear 35d that rotates integrally with the branch transmission shaft 35, and the left and right drive shafts 20, 20 are driven through the differential device 3D. The driving force is transmitted to the front axles 2a and 2a.
The branch transmission shaft 35 is also provided with a second transmission gear 35e so as to rotate integrally therewith, and a driving force is branched and transmitted to the relay transmission shaft 38 via a transmission gear 38a meshing with the second transmission gear 35e. The power of the branch transmission shaft 35 is branched and transmitted to the rear wheel drive shaft 39 via a bevel gear 38b provided on the relay transmission shaft 38 and a bevel gear 39a meshing with the bevel gear 38b.

(Hydraulic system)
Various hydraulic actuators to which pressure oil from the gear pump 25 is supplied are configured as shown in FIG.
That is, in the gear pump 25, as shown in FIG. 18, the oil stored in the mission case 30 passes through the strainer 26a provided near the bottom surface 30e of the mission case 30, and the oil supply passage 26 connected to the strainer 26a. It is configured to inhale through.
The oil sucked into the oil supply passage 26 is supplied as charge oil to the closed circuit of the hydrostatic continuously variable transmission 3A through the first oil passage r1, and is also supplied to the power steering device through the second oil passage r2. 60, the cutting lift cylinder 27, the reel lifting cylinder 28, and the dump cylinder 29 for lifting and lowering the Glen tank 5.

  The first oil passage r1 connected to the closed circuit of the hydrostatic continuously variable transmission 3A is supplied so as to compensate for the shortage of the oil amount in the closed circuit of the hydrostatic continuously variable transmission 3A. On the path r2, a cutting lift valve 28b for controlling the operation of the cutting lift cylinder 27 is operated in accordance with the operation of the lifting lever (not shown), and the operation of the reel lifting cylinder 28 is controlled in accordance with the operation of the reel lifting lever (not shown). The reel lift valve 28c is operated, and the dump operation valve 29a for controlling the operation of the dump cylinder 29 is operated in accordance with the operation of the dump operation lever (not shown).

  The oil in the second oil passage r2 is also supplied to the power steering device 60. The operation of the power steering device 60 is a steering operation amount detector 64 that detects the operation of the steering handle 15a, and the drive transmission shaft 24. It is configured to be controlled by a power steering control valve 60c that operates based on a detection signal of a drive speed detector 65 that detects the rotational speed of the motor.

[Other Embodiment 1]
In the above embodiment, the power source of the engine 8 is used as the power source, but the power source is an electric motor driven by a power generation device such as a battery or a hydrogen power generation device. Also good.
Other configurations may be the same as those in the above-described embodiment.

[Second embodiment]
In the above-described embodiment, the traveling device 2 is configured such that the front wheel 2F is configured by a non-steering wheel and the rear wheel 2R is configured by a steering wheel. However, the present invention is not limited thereto, and for example, the front wheel 2F is steered. The rear wheel 2R may be a non-steering wheel.
In the embodiment, both the front wheel 2F and the rear wheel 2R are configured as drive wheels. However, the present invention is not limited thereto, and only non-steering wheels are configured as driving wheels, and steering wheels are configured as non-driven wheels. Also good.
Other configurations may be the same as those in the above-described embodiment.

[3 of another embodiment]
In said embodiment, the thing of the structure by which the whole lower surface side of the threshing apparatus 4 is illustrated is illustrated, and the threshing apparatus 4 is arranged at the position where the rear wheel transmission shaft 24 is removed from the lower surface of the threshing apparatus 4. Although the structure of the structure that facilitates maintenance in the open state on the lower surface side of the is shown, it is not limited to such a structure. For example, in the structure in which a part of the lower surface side is partially opened rather than the entire lower surface side of the threshing device 4, the rear wheel transmission shaft 24 exists at a position deviated from the open area on the lower surface side. You may make it arrange | position so.
Other configurations may be the same as those in the above-described embodiment.

[4 of another embodiment]
In the embodiment described above, the drive transmission shaft 24 is used as the drive transmission tool. However, the drive transmission tool is not limited to transmission using a shaft, and may be a transmission chain or a transmission belt.
Other configurations may be the same as those in the above-described embodiment.

[5 of another embodiment]
In the above embodiment, the gear pump 25 is configured to be driven by the branched power from the input shaft 31. However, the present invention is not limited to this. For example, power before being input to the mission case 30 is taken out. Alternatively, the gear pump 25 may be driven. In this case, the gear pump 25 may be provided separately from the mission case 30.
Other configurations may be the same as those in the above-described embodiment.

[6 of another embodiment]
In the above embodiment, the structure is shown in which the parking brake 18 is mechanically pressed by depressing the parking brake pedal. However, the present invention is not limited to this. For example, the friction plate 18a of the parking brake 18 is braked by a spring member (not shown). It may be configured such that the biasing force by the spring member is released by hydraulic pressure.
Other configurations may be the same as those in the above-described embodiment.

[7 of another embodiment]
In the above embodiment, as the transmission gear 34c of the auxiliary transmission, the three kinds of gear portions g1, g2, and g3 of the high speed gear portion g1, the medium speed gear portion g2, and the low speed gear portion g3 are individually provided. In the shift operation mechanism 7, each gear is always engaged with the high-speed gear 35 a, the medium-speed gear 35 b, and the low-speed gear 35 c on the branch transmission shaft 35 side so that power transmission is performed alternatively. Although the one in which the power of the transmission shaft 34 is transmitted to any one of the parts g1, g2, and g3 is shown, it is not limited to such a mechanism. For example, three kinds of gear parts g1, g2, and g3, which are a high speed gear part g1, a medium speed gear part g2, and a low speed gear part g3, are provided in a transmission gear 34c formed of a single member, and the speed change is performed. The entire transmission gear 34c is shifted in the axial direction of the speed change transmission shaft 34 so as to selectively mesh with the high speed gear 35a, the medium speed gear 35b, and the low speed gear 35c on the branch transmission shaft 35 side. It may be configured.
Further, the shift speed of the auxiliary transmission is not limited to the above-described three shift speeds, but may be provided with two or more shift speeds, or four or more shift speeds including ultra-low speed.
Other configurations may be the same as those in the above-described embodiment.

[8 of another embodiment]
In the above embodiment, as the shift operating mechanism 7, the recesses 75b and 76b are formed in the boss portions 75a and 76a of the shift operating members 75 and 76, respectively, and a plurality of steel balls 77 are provided between the recesses 75b and 76b. Is configured so that only one shift operation member 75 (or 76) of the shift operation members 75 and 76 can be operated, but the present invention is not limited to this. For example, you may comprise the structure which performs the same check using the bar material of the length equivalent to the length of the aligned direction of the some steel ball 77, for example. Moreover, even if it uses a completely different check structure, it does not matter.
Other configurations may be the same as those in the above-described embodiment.

[9 of another embodiment]
In the above embodiment, the Glen tank 5 is configured to swing around the swing axis z2 of the right lateral side that is one lateral side in the left-right direction, and the stored grain is discharged. For example, it may be configured as shown in FIG.
That is, the Glen tank 5 itself is connected and fixed to the support leg 12 and the threshing device 4 and mounted in a fixed position with respect to the vehicle body frame 1, and the end of the Glen tank 5 on the side far from the opening portion provided with the opening / closing lid 51. The bottom surface member 53 is configured to be partially swingable, and the end portion of the bottom surface member 53 is lifted and stored so as to swing around the swing axis z3 on the side close to the opening portion. You may enable it to discharge | emit a grain.
Other configurations may be the same as those in the above-described embodiment.

[10 of another embodiment]
In the above embodiment, the input pulley 31a to which the power from the engine 8 is input is shown to be provided at the end of the input shaft 31 of the transmission 3. However, the present invention is not limited to this. For example, FIG. You may comprise as shown.
That is, when the extending direction of the output shaft 8a of the engine 8 and the extending direction of the input shaft 31 of the transmission 3 are the same direction, the input pulley 31a is connected to the pump shaft of the hydrostatic continuously variable transmission 3A. Instead of the input shaft 31 concentric with 33, the counter shaft 84 may be provided on a counter shaft 84 different from the input shaft 31, and the counter shaft 84 and the input shaft 31 may be gear-linked. In this case, it is easy to simplify the structure if the counter shaft 84 is configured to also serve as an input means for the pump drive shaft 25a of the gear pump 25.

As shown in FIG. 12, the input pulley 31a is attached to the counter shaft 84 different from the input shaft 31 concentric with the pump shaft 33 of the hydrostatic continuously variable transmission 3A. In the case where the extending direction of the shaft 8a and the extending direction of the input shaft 31 of the transmission 3 are opposite to each other, the hydrostatic non-rotating state is the same as the predetermined rotating direction of the hydrostatic continuously variable transmission 3A. This is because the step transmission 3A is rotationally driven.
Other configurations may be the same as those in the above-described embodiment.

  The harvester shown in the present invention is not limited to a combine harvester that harvests grains such as rice, wheat, and corn, but can also be applied to a harvester that harvests beans such as soybeans and florets such as rapeseed.

1 Body frame 2 Wheel traveling device 2F Front wheel (non-steering wheel)
2R rear wheel (steering wheel)
DESCRIPTION OF SYMBOLS 3 Transmission 3A Hydrostatic continuously variable transmission 3B Planetary gear reduction device 4 Threshing device 5 Glen tank 8 Engine 17A Feeder 18 Parking brake 20 Output shaft 26 Oil supply path 26a Strainer 27, 28, 29 Hydraulic equipment 30 Mission case 30c Upper surface 30g Hook Part 31 Input shaft 34, 35 Each transmission shaft 35 Branch transmission shaft a Virtual line segment p1 axis center p2 axis center

Claims (10)

An input shaft extending in the left-right direction is arranged on one end side in the front-rear direction on the upper side of the mission case, and in the left-right direction on the other end side opposite to the one end portion on the lower side of the mission case. Along the output shaft,
Each transmission shaft in the power transmission system from the input shaft to the output shaft is below the imaginary line connecting the axis of the input shaft and the axis of the output shaft, and the one end side of the transmission case A transmission for a harvester disposed along a vertical direction closer to the bottom and a horizontal direction closer to the bottom side of the mission case.   The power transmission system from the input shaft to the output shaft includes a hydrostatic continuously variable transmission and a planetary gear reduction device using a planetary gear mechanism, and the power input to the hydrostatic continuously variable transmission. And the power output from the hydrostatic continuously variable transmission is input to the planetary gear reduction device, and the output from the planetary gear reduction device is transmitted to the lower transmission side. The transmission for the described harvester.   The transmission for a harvester according to claim 1 or 2, wherein an inclined surface is formed on an upper surface of the mission case so that the other end side is lower than the one end portion.   An oil supply path strainer is provided at a position lower than the outer peripheral edge of the gear mounted on each transmission shaft in the output shaft and the power transmission system to suck the stored oil in the transmission case and guide it to hydraulic equipment. The transmission according to any one of claims 1 to 3.   A harvester using the transmission for a harvester according to any one of claims 1 to 4, wherein the transmission case is disposed in a posture in which an output shaft is positioned in front of the input shaft. The harvester is characterized in that a feeder for feeding and transporting the harvested crop is located above the mission case and is disposed so as to overlap the mission case in plan view.   6. The feeder according to claim 5, wherein the feeder is disposed within a width in the left-right direction between the left and right wheels of the wheel traveling device and at a position deviated laterally from a center position in the left-right direction of the vehicle body. Harvester.   The harvesting machine according to claim 6, wherein the mission case is disposed at a position opposite to a side where the feeder is biased within a width in a left-right direction between left and right wheels.   The harvesting machine according to claim 6 or 7, wherein an operation mechanism from the outside for the power transmission system in the mission case is provided at an end of the mission case opposite to a side where the feeder is biased.   The harvester according to any one of claims 6 to 8, wherein the feeder includes a threshing device that supplies a harvested crop, and the threshing device is disposed at a position on a side where the feeder is biased.   The hook part for suspension is provided in the upper part of the said mission case, The engaging part which can lift the said mission case via the said hook part is provided in the said feeder. The harvesting machine described.

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