WO2005058010A1

WO2005058010A1 - Combine

Info

Publication number: WO2005058010A1
Application number: PCT/JP2004/018875
Authority: WO
Inventors: Wataru Nakagawa; Tomohiro Koyama; Mitsuteru Oonishi
Original assignee: Yanmar Co., Ltd.; Seirei Industry Co., Ltd.
Priority date: 2003-12-19
Filing date: 2004-12-17
Publication date: 2005-06-30
Also published as: JPWO2005058010A1; CN100493330C; KR20060110732A; KR101114885B1; CN1764369A; JP4341971B2

Abstract

A combine not threshing grains from ears of cereal columns while the reaping portion is raising the cereal columns during low-speed traveling harvesting work and not lowering the efficiency of high-speed traveling harvesting work. The drive speed of a reaping portion is switched to either a car-speed synchronous speed copying after a car-speed synchronous pattern which is synchronous with the car speed and increases in proportion to an increase of the car or a predetermined rotational speed generally constant irrespective of the variation of the car speed, and the reaping portion is driven. The combine is characterized by comprising a car-speed sensor for detecting the car speed, a reaping input sensor for detecting the rotational speed of the input shaft driving the reaping portion and switching means for switching the drive speed of the reaping portion to one of a constant low speed, the car-speed synchronous speed, and a constant high speed.

Description

Specification

Conno Inn

Technical field

The present invention relates to, for example, a combine that moves by mounting a pair of left and right traveling crawlers.

Background art

[0002] Conventionally, a transmission case that drives the traveling crawler, a reaping unit, and a threshing unit are provided. The driving force from the engine is transmitted to the threshing unit, the reaping unit, and the transmission case, respectively. There is a technique in which the harvester is driven by either a vehicle speed synchronizing speed output from the transmission case or a substantially constant speed output from an engine to perform a harvesting operation (for example, see Patent Document 1).

[0003] Conventionally, for example, when turning (turning direction) on a field headland, the driving speed of the cutting unit is switched from the vehicle speed synchronization speed to a low constant speed, and the culm of the cutting unit is transferred to the threshing unit. out and had prevented稈詰Ri and the like in the reaper (e.g., see Patent Document 2) ₀

Patent Document 1: Japanese Patent Application Laid-Open No. 10-286018

Patent Document 2: JP-A-10-127146

Disclosure of the invention

Problems to be solved by the invention

[0004] When the grain culm is cut at the low constant speed, when the cereal culm transport speed in the reaping unit becomes faster than the vehicle speed (moving speed of the combine), the culm tip of the cereal culm becomes larger than the grain culm in the cutting unit. There was a problem such as being handled during the raising operation and causing threshing.

[0005] On the other hand, when harvesting is performed at a high speed, since the driving loads of the traveling crawler and the reaping unit for transmitting the driving force from the transmission case become large, the driving load becomes overloaded, and the high speed traveling becomes difficult. There was a problem that the efficiency of the harvesting operation at the time was reduced.

[0006] In view of such a conventional problem, the present invention considers that when performing a low-speed traveling harvesting operation, the ears of the cereal culm are handled by the culm raising operation of the cutting section and shed. While performing high-speed harvesting work, a combine that prevents the work efficiency from lowering It is intended to provide.

Means for solving the problem

[0007] In order to achieve the above object, the invention according to claim 1 provides a vehicle speed tuning speed according to a vehicle speed tuning pattern that synchronizes the drive speed of the reaper with the vehicle speed and increases in proportion to the increase of the vehicle speed. A combiner configured to drive the reaping unit by switching to one of a preset substantially constant rotation speed regardless of the increase or decrease of the vehicle speed, a vehicle speed sensor for detecting the vehicle speed, and a drive for the reaper. Switching means for switching the speed to one of a low constant speed, a vehicle speed synchronizing speed, and a high constant speed.

[0008] The invention according to claim 2 is the invention, wherein the low-speed constant speed corresponds to a case where the vehicle speed in the vehicle speed tuning section is a lower shift point at which the driving speed of the reaping unit is switched to a low-speed constant speed. The drive speed is set higher than the drive speed.

[0009] The invention according to claim 3 is characterized in that the high-speed constant speed corresponds to a time when the vehicle speed in the vehicle speed tuning section is a higher-order transposition point at which the driving speed of the mowing unit is switched to a high-speed constant speed. The drive speed is set higher than the drive speed.

[0010] The invention according to claim 4 is characterized in that the switching means switches the driving speed of the reaping unit from a vehicle speed tuning speed to a constant low speed when the switching device is operated to switch backward. Is controlled.

[0011] The invention according to claim 5 is characterized in that the reaping unit is driven at a vehicle speed tuning drive for changing the reaping speed in synchronization with the vehicle speed or at a constant pouring drive speed for keeping the reaping speed substantially constant. The speed of the pouring drive is switched between high speed and low speed in two stages, and the mowing unit is driven at the high or low constant pouring drive speed.

[0012] The invention according to claim 6 is that the vehicle speed tuning speed of the reaper that switches from the vehicle speed tuning drive to a high-speed constant speed pouring drive speed is lower than the low-speed constant speed pouring drive speed. It is configured as follows.

The invention's effect

[0013] The invention according to claim 1 includes switching means for switching the drive speed of the reaping unit to one of a low constant speed, a vehicle speed tuning speed, and a high constant speed. Therefore, it is possible to prevent the ears of the grain culm from being handled and threshing in raising the grain culm of the cutting section in the low-speed traveling harvesting work. On the other hand, it is possible to prevent overload in high-speed harvesting work. Therefore, in any of the low-speed traveling harvesting operation and the high-speed traveling harvesting operation, the reaper can be appropriately driven at the low-speed constant speed or the high-speed constant speed, and the reaping workability of the low-speed traveling harvesting operation is improved. In addition, the efficiency of high-speed harvesting can be improved.

[0014] The invention according to claim 2 is characterized in that the low speed constant speed corresponds to a time when the vehicle speed in the vehicle speed tuning section is a lower shift point at which the driving speed of the mowing unit is switched to the low speed constant speed. Since the driving speed is set higher than the driving speed, when the mowing unit is driven at the vehicle speed tuning speed according to the vehicle speed tuning pattern, the driving speed of the mowing unit is lower than the low speed constant speed. Thus, even if the vehicle speed in the vehicle speed tuning section is temporarily reduced to near the lower shift point, the driving speed of the cutting unit is maintained at the vehicle speed tuning speed according to the vehicle speed tuning pattern, and the head of the grain culm is harvested. It can be prevented from being thrown out by being handled during the raising operation of the part.

[0015] The invention according to claim 3 is characterized in that the high-speed constant speed corresponds to a case where the vehicle speed in the vehicle speed tuning section is a higher-order transposition point at which the driving speed of the reaping unit is switched to a high-speed constant speed. Since the driving speed is set higher than the driving speed, the driving speed of the mowing unit is switched from the vehicle speed tuning speed according to the vehicle speed tuning pattern to the high-speed constant speed with a margin for the engine output. be able to. When the reaping unit is driven at a vehicle speed tuning speed along a vehicle speed tuning pattern, it is possible to smoothly shift to the high-speed running harvesting operation in which the reaping unit is driven at the high-speed constant speed. Work efficiency can be improved.

[0016] The invention according to claim 4 is characterized in that the switching means switches the drive speed of the reaping unit from a vehicle speed tuning speed to a constant low speed when the switching device is operated to switch backward. Is controlled. At the time of reversing, the reaping unit is in a stopped state. Therefore, even if the reaping unit is driven from a stopped state, the driving of the reaping unit is started at a low speed and a constant speed. It is possible to suppress the impact load when starting the driving of the motor. [0017] The invention according to claim 5 is characterized in that the reaping unit is driven by a vehicle speed tuning drive for changing the harvesting speed in synchronization with the vehicle speed or a pouring drive speed of a constant speed for keeping the harvesting speed substantially constant. Since the pouring drive speed is switched between high speed and low speed in two stages, and the mowing unit is driven at the above-mentioned constant pouring drive speed of high speed or low speed, the harvesting operation at low speed or high speed In any of the traveling and harvesting operations, the cutting section can be appropriately driven at the low-speed constant speed or the high-speed constant speed, so that the harvesting workability of the low-speed traveling and harvesting operation can be improved and the high-speed traveling and harvesting operation can be performed. Work efficiency can be improved.

[0018] In the invention according to claim 6, the vehicle speed tuning speed of the reaping unit that switches from the vehicle speed tuning drive to the high-speed constant speed pouring drive speed is lower than the low-speed constant speed pouring drive speed. With such a configuration, the drive speed of the reaping unit is increased by the switching operation of the operator over the entire range of the vehicle speed tuning speed of the reaping unit, and the operator can perform the driving operation without a sense of incongruity.

Brief Description of Drawings

FIG. 1 is a left side view of the combine.

FIG. 2 is a plan view of the same.

FIG. 3 is a right side view of the same.

FIG. 4 is an explanatory front view of a front body.

FIG. 5 is an explanatory plan view of a machine base.

FIG. 6 is an enlarged view of a counter case part.

FIG. 7 is a side view of the front body.

FIG. 8 is an enlarged view of the same part.

FIG. 9 is a side view of a counter case part.

FIG. 10 is an output system diagram of the engine.

FIG. 11 is a drive system diagram of a transmission case.

FIG. 12 is a hydraulic circuit diagram.

FIG. 13 is a sectional view of a counter case.

FIG. 14 is the same drive system diagram. FIG. 15 is a modified explanatory view of FIG. 13.

FIG. 16 is a drive system diagram of the previous figure.

FIG. 17 is a sectional view of a torque limiter unit.

FIG. 18 is an exploded view of the same part.

FIG. 19 is an exploded enlarged view of the same part.

FIG. 20 is an enlarged view of the same portion.

FIG. 21 is a control circuit diagram.

FIG. 22 is a flowchart of cutting section speed control.

FIG. 23 is a diagram showing a relationship between a cutting speed KVx of a cutting transmission shaft for driving a cutting unit and a vehicle speed SV.

[Fig.24] The cutting speed KVx of the cutting power transmission shaft and the vehicle speed S when the speed of the cutting unit is high and low.

FIG. 4 is a diagram showing a relationship with V.

FIG. 25 is a control circuit diagram.

FIG. 26 is an explanatory diagram of a display screen of a liquid crystal panel.

FIG. 27 is an explanatory diagram of a display screen of a liquid crystal panel.

FIG. 28 is a flowchart of high-speed cut control.

FIG. 29 is an output diagram of high-speed cut control.

FIG. 30 is a flowchart of cutting quick control.

FIG. 31 is an output diagram of reaping quick control.

FIG. 32 is a flowchart of a harvesting operation control.

Explanation of symbols

[0020] 7 Harvester

112 input shaft

277 Pouring pedal (switching means)

285, 286 Vehicle speed sensor

288 Cutting input sensor

BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. Figure 1 shows the entire combine 2 is a plan view, and FIG. 3 is a right side view of the same.

[0022] The combine to which the present invention is applied includes a pair of left and right track frames 1 on which a pair of left and right traveling crawlers 2 are mounted, a machine installed between the left and right track frames 1, and a feed chain 5 on the left side. A threshing unit 4 that has a handling cylinder 6 and a processing cylinder 6a, and a cutting unit 7 in which a raising mechanism 8, a cutting blade 9, and a culm transport mechanism 10 are arranged. A hydraulic elevating cylinder 11 connected to the frame 12, a straw processing unit 13 facing the end of the straw chain 14, a grain tank 15 for bringing in the grains from the threshing unit 4 through a graining cylinder 15a, and the grain. Vertical and horizontal discharge augers 16 and 17 for transporting the grains in the tank 15 out of the machine, a driving cabin 18 with a driving operation handle 19 and a driver's seat 20 inside, and an engine 21 installed below the driving cabin 18 And continuously harvest and thresh the culm in the field. It is configured so as.

With reference to FIGS. 4 to 10, the configuration of the combine body of the present invention will be described. The transmission case 22 is arranged between the left and right traveling crawlers 2 in front of the machine base 3. The transmission case 22 and the engine 21 are installed in front and behind in substantially series, and the driving force from the engine 21 is transmitted to the traveling crawler 2 via the transmission case 22.

[0024] On the upper surface of the machine base 3 in front of the threshing unit 4, left and right support bases 23 and 24 are erected. A cutting section 7 is installed on the left and right support bases 23 and 24 via a cutting frame 12 so as to be able to move up and down and move laterally. A counter case 25 is installed on the upper surface of the machine 3 on the rear side of the left and right support bases 23, 24 so that the driving force from the engine 21 is transmitted to the threshing unit 4 and the reaping unit 7 via the counter case 25. Configure (see Figure 10).

As shown in FIGS. 4 and 7, a cabin front frame 26 is erected on the machine base 3 on the side of the transmission case 22. The upper part of the cabin front frame 26 is installed on the front part of the step frame 27 of the cabin 18 via the rotation fulcrum shaft 28. The cabin 18 is connected to an upper portion of the cabin front frame 26 via a pivot shaft 28.

[0026] On the right support stand 24, a rear cabin rear frame 29 is erected. The engine 21 is installed on the upper surface of the machine 3, and the engine 21 is arranged between the right rear cabin rear frame 30 and the left cabin rear frame 29 erected on the machine 3. Install the engine room cover 31 that covers the engine 21 (see Fig. 4). Further, the upper portions of the left and right rear cabin rear frames 29, 30 are connected by a cabin horizontal frame 32, and the cabin horizontal frame 32 is arranged above the engine room cover 31. The rear part of the step frame 27 and the cabin side frame 32 are detachably connected via the base bracket 33 (see FIG. 4).

[0028] The horizontal connection frame 34 is disposed between the right support base 24 and the cabin front frame 26.

On the other hand, the inclined connecting frame 35 is connected to the horizontal connecting frame 34 and the cabin lateral frame 32, and the horizontal and inclined connecting frames 34 and 35 are configured to secure the rigidity of the front cabin frame 26 (FIG. 5). reference).

Further, the auger post 36 is connected to the rear cabin rear frame 29, and an auger rest 37 for supporting the vertically movable and revolvable discharge auger 17 at the storage position of the machine is installed above the auger post 36. (See Figure 7).

Further, a configuration for transmitting the driving force of the engine 21 to the transmission case 22 will be described with reference to FIGS. 10 to 12. The transmission case 22 includes a traveling transmission member 40 forming a hydraulic continuously variable transmission mechanism for traveling main transmission composed of a pair of hydraulic traveling pumps 38 and a hydraulic traveling motor 39, a pair of hydraulic swing pumps 41 and a hydraulic swing motor. And a turning member 43 forming a hydraulic stepless speed change mechanism for turning composed of 42. The input shaft 45 of the transmission case 22 is connected to the output shaft 44 of the engine 21. The traveling pump 38 and the swirl pump 41 are configured to be driven by the output from the engine 21.

The differential mechanism 48 has a pair of left and right symmetric planetary gear mechanisms 50. Each planetary gear mechanism 50 is composed of one sun gear 51, three planetary gears 52 that match around the outer periphery of the sun gear 51, and a ring gear 53 that matches these planetary gears 52 (see FIG. 11).

[0032] Left and right carriers 56 for rotatably supporting the planetary gear 52 are installed on the left and right axles 55 coaxial with the idle shaft 54 of the sun gear 51. The left and right carriers 56 are arranged to face each other so as to sandwich the left and right sun gears 51. On the other hand, a ring gear 53 having internal teeth that mesh with each planetary gear 52 is rotatably supported on an axle 55. The drive wheels 49 are pivotally supported on an axle 55, and the respective drive wheels 49 of the left and right traveling crawlers 2 are connected to the motor shaft 46 of the traveling motor 39 via the auxiliary transmission mechanism 47 and the differential mechanism 48. (See Figure 11).

[0033] The traveling speed change member 40 changes the forward / reverse direction of the traveling motor 39 by changing the swash plate angle of the traveling pump 38. It is configured to control the rotation and the number of rotations. The rotation of the traveling motor 39 is transmitted to the left and right ring gears 53 via the motor shaft 46, the low and high speed gears 57 and 58 of the auxiliary transmission mechanism 47, the brake shaft 59 and the branch shaft 60, and the left and right carrier 56 Is rotated (see Fig. 11). The parking brake 61 is arranged on the brake shaft 59.

On the other hand, a mowing drive pulley 62 for transmitting a rotational force to the mowing unit 7 is installed on the motor shaft 46. The mowing unit 7 is configured to be driven at the vehicle speed tuning speed via the mowing drive pulley 62 (see FIG. 11).

As described above, the driving force of the traveling motor 39 is transmitted to the ring gear 53 via the branch shaft 60, transmitted to the left and right carriers 56 via the left and right planetary gear mechanisms 50, and transmitted via the left and right carriers 56. The left and right driving wheels 49 are transmitted to the left and right driving wheels 49, respectively, so that the left and right traveling crawlers 2 are driven in the same direction and at the same speed (see FIG. 11).

The steering output brake 63 is arranged on the motor shaft 64, the steering output clutch 65 is arranged on the clutch shaft 66, and the left and right input gears 67 and 68 are always engaged with the left and right sun gears 51. On the other hand, the clutch shaft 66 is connected to the left and right input gears 67 and 68 via the motor shaft 64 for outputting the turning motor 42 and the steering output clutch 65. The left and right input gears 67, 68 are connected to the clutch shaft 66 via the forward rotation gear 69 and the reverse rotation gear 70 (see FIG. 11).

[0037] While the rotational force of the motor 42 is transmitted to the right sun gear 51 via the forward rotation gear 69, the rotational force of the motor 42 is transmitted to the left sun gear 51 via the reverse rotation gear 70 to rotate the rotation motor 42 forward (reverse rotation). The left sun gear 51 rotates forward (forward) at the same rotational speed as the left and right, while the right sun gear 51 rotates forward (reverse) and drives the left and right traveling crawlers 2 in the opposite direction at the same speed. It is configured so that Further, the turning member 43 forming the turning hydraulic continuously variable transmission mechanism is configured to control the forward / reverse rotation and the rotation speed of the turning motor 42 by changing the swash plate angle of the turning pump 41. (See Figure 11).

Therefore, when the turning motor 42 is stopped and the left and right sun gears 51 are stopped, when the traveling motor 39 is driven, the rotation of the traveling motor 39 is transmitted to the left and right ring gears 53 at the same rotation speed. Therefore, the right and left traveling crawlers 2 receive the driving force of the same rotational direction and the same rotational speed via the carrier 56, so that the aircraft travels in the front-rear direction by the driving of the left and right traveling crawlers 2. (See Figure 11). On the other hand, when the traveling motor 39 is stopped and the left and right ring gears 53 are stopped, when the rotation motor 42 is driven in the forward rotation (or reverse rotation) direction, the left planetary gear mechanism 50 rotates forward (or On the other hand, the right planetary gear mechanism 50 rotates in the reverse direction (or forward rotation) to drive the left and right traveling crawlers 2 in opposite directions. (See Fig. 11).

[0040] On the other hand, when both the traveling motor 39 and the turning motor 42 are driven at the same time, the body moves forward and rearward and turns left and right, so that the course of the body can be corrected. The turning radius of the body is configured to be determined by the output rotation speed of the turning motor 42.

As shown in FIGS. 10 and 11, a cooling fan 72 for a water cooling radiator of the engine 21 is provided, the cooling fan 72 is arranged on the fan shaft 71, and the fan shaft 71 is connected to the input shaft 45. The fan shaft 71 is connected to the pump shafts 73, 74 of the traveling and swirling pumps 38, 41 via a gear group 75. An input shaft 45 is connected to each pump 38,41. A pump shaft 73 of the traveling pump 38 and a motor shaft 46 of the traveling motor 39 are connected to a constant speed shaft 77 via a constant vehicle speed clutch 76. When the vehicle speed constant speed clutch 76 is engaged, the pump shaft 73 and the motor shaft 46 are gear-connected via the constant speed shaft 77.

[0042] The rotation of the input shaft 45 is transmitted to the sub-transmission mechanism 47 without passing through the traveling transmission member 40, and the left and right traveling crawlers 2 are driven by the constant speed rotation of the engine 21 to travel at a substantially constant vehicle speed. To perform harvesting work (see Fig. 11). The charge pump 78 is connected to the swivel pump shaft 74.

Further, a hydraulic circuit for driving the traveling motor 39 will be described with reference to FIG. A swash plate 79 of the traveling pump 38 A main transmission cylinder 80 that adjusts the output by changing the angle, a transmission valve 82 that is switched by the main transmission lever 81 and the steering handle 19, and a valve that reduces the output of the traveling pump 38 by a certain amount 83 and installed. The charge pump 78 is formed so as to be hydraulically connected to the main transmission cylinder 80 via the valves 82 and 83.

When the shift valve 82 is switched by the main shift lever 81, the main shift cylinder 80 operates to change the angle of the swash plate 79 of the traveling pump 38, thereby reducing the rotation speed of the motor shaft 46 of the traveling motor 39. While performing a traveling shift operation in which the speed is changed in steps or reverses, a feedback operation is performed so that the shift valve 82 returns to neutral by the angle adjustment operation of the swash plate 79, and the The angle of the swash plate 79 changes in proportion to the operation amount of the main shift lever 81, and the rotation speed of the traveling motor 39 changes to change the vehicle speed (see FIG. 12).

As shown in FIG. 12, a sub-transmission cylinder 85 for adjusting the output by changing the angle of the swash plate 84 of the traveling motor 39 is installed, and the sub-transmission cylinder 85 is electromagnetically connected to the charge pump 78. It is formed so as to be hydraulically connected via the auxiliary transmission valve 86. When the sub-transmission valve 86 is in the neutral position, the sub-transmission cylinder 85 is short-circuited to the transmission case 22, which is an oil tank, to change the angle of the swash plate 84 of the traveling motor 39 by the main circuit oil pressure. The output of the traveling motor 39 is changed to a high speed or a low speed by forcibly changing the angle by switching the subtransmission valve 86.

Further, as shown in FIG. 12, a swash plate 87 of the slewing pump 41 is connected to a slewing cylinder 88 for adjusting the output by changing the angle, a steering handle 19 and a main speed change lever 81. The swing valve 89 and the electromagnetic automatic steering valve 90 that are switched by the operation of are installed. A charge pump 78 is formed to be hydraulically connected to a swivel cylinder 88 via a swivel valve 89 and an electromagnetic self-steering valve 90.

When the swivel valve 89 is switched by the steering handle 19, the swivel cylinder 88 is operated to change the angle of the swash plate 87 of the swivel pump 41, and the rotational speed of the motor shaft 64 of the swivel motor 42 is steplessly changed. The swash plate 87 is angle-controlled by performing a feedback operation so that the swivel valve 89 returns to a neutral position in the angle adjustment operation of the swash plate 87 while performing a left-right swing operation of changing or reversing the swash plate 87. The rotation amount changes in proportion to the operation amount of 19, and the rotation speed of the rotation motor 42 changes to change the left-right rotation angle (see FIG. 12).

When the main shift lever 81 is operated to a position other than neutral and the steering handle 19 is operated to a position other than straight ahead, the hydraulic output of the traveling pump 38 changes the operating direction of the main shift lever 81 and the operation direction. When the forward / backward speed (vehicle speed) is changed by forward / reverse rotation or acceleration / deceleration of the hydraulic motor 39, the output of the swing pump 41 changes in proportion to the operation amount of the main shift lever 81. (See Figure 12).

[0049] When the main shift lever 81 is operated, the turning radius is automatically reduced in the high-speed running shift, and the turning radius is automatically increased in the low-speed running shift. , The turning radius of the left and right traveling crawler 2 becomes almost constant regardless of the traveling speed. It will be maintained and the work speed will be changed, and the course will be adjusted to make the aircraft follow the uncut culm row.

On the other hand, when each of the valves 82 and 89 is controlled, the output of the turning pump 41 and the output of the traveling pump 38 change in proportion to the operation amount of the steering handle 19, and the turning radius (steering angle) If is made smaller (larger), the traveling speed (vehicle speed) is reduced proportionally, and the speed difference between the left and right traveling crawlers 2 is increased, and the vehicle turns left and right.

[0051] Therefore, by changing the driving speed of the left and right traveling crawlers 2, correcting the alignment path and changing the direction by spin turn at the headland of the field, the harvesting work of continuously cutting and threshing the grain culm is performed. Will do. When the main shift lever 81 is in the neutral position, the swing valve 89 related to the operation of the steering hand lever 19 is maintained in the neutral position, the hydraulic output of the swing pump 41 is maintained at substantially zero, and the swing motor 42 is stopped. To be configured.

Next, a transmission structure of the counter case 25 will be described with reference to FIGS. 10 to 14. The output shaft 44 of the engine 21 protrudes from the front and rear sides of the counter case 25. The front side of the output shaft 4 is connected to the input shaft 45. A work output pulley 91 is disposed behind the output shaft 44. A counter case 25 is installed on the machine base 3 on the left side of the engine 21 and in front of the threshing unit 4. The counter case 25 includes an input pulley 92, a vehicle speed tuning pulley 93, a threshing pulley 94, a cutting pulley 95, and a sorting pulley 96. Work the input pulley 92 on the rear side of the counter case 25 with the belt 98 via the tension pulling clutch 97 to the output pulley 91 so that the driving force from the engine 21 is transmitted to the counter case 25 via the input pulley 92. To be configured.

[0053] The vehicle speed tuning pulley 93 on the right side of the counter case 25 is connected via a idle pulley 99 on the front side of the right support stand 24 to a horse pulling pulley 62 of the transmission case 22. A cutting input pulley 103 is pivotally supported on the left side of the case 101 via a cutting input shaft 102, and a cutting pulley 95 on the left side of the counter case 25 is connected to a male IJ input pulley 103 with a belleto 104. It is configured to transmit the driving force to each part of Fig. 7 (see Fig. 10). The mowing input case 101 is rotatably supported on the support bases 23 and 24, the mowing frame 12 is connected to the case 101, and the mowing portion 7 is rotated around the case 101 to move up and down. I do.

Next, the threshing pulley 94 on the front side of the counter case 25 is connected to the drive input pulley 105 of the handling cylinder 6. The belt 106 is connected to the belt 106, and the driving force from the sorting pulley 96 is transmitted to the sorting machine and the swing sorting mechanism on the lower side of the handling cylinder 6 to drive each part of the threshing unit 6. On the other hand, a feed chain input shaft 107 is provided on the left side surface of the counter case 25, and a driving sprocket 108 of the feed chain 5 is disposed so as to be movable to the outside on the feed chain input shaft 107, so that the power from the input shaft 107 is Is transmitted to the drive sprocket 108 (see FIG. 10).

On the other hand, a discharge drive pulley 109 is installed on the front side of the grain tank 15. The pulley 109 is connected to the work output pulley 91 by a belt via a discharge clutch 110 so that the output from the engine 21 is transmitted to the discharge auger 17 to discharge the grains in the tank 15 (see FIG. 10). ).

As shown in FIG. 14, the handle cylinder input shaft 111 is supported by the counter case 25, and the shaft 111 extends in the front-rear direction of the counter case 25. A threshing pulley 94 is installed at the front end of the shaft 111 projecting outside the front of the counter case 25, while an input pulley 92 is installed at the rear end of the shaft 111 projecting outside the rear of the counter case 25, A constant rotational power from the engine 21 is input to the cylinder input shaft 111 to rotate the input shaft 111 at a constant speed.

On the other hand, the tuning input shaft 112 is pivotally supported on the right side of the counter case 25, the tuning input shaft 112 protrudes to the right outside of the counter case 25, and the vehicle speed tuning pulley 93 is disposed at the right end of the shaft 112. Then, the belt 100 is tensioned between the pulleys 62 and 93 via the idle pulley 99 so that the vehicle speed tuning power is input from the transmission case 22 to the counter case 25 (see FIG. 10).

Further, a constant speed shaft 114 which is a counter shaft or a sorting input shaft connected to the handle cylinder input shaft 111 via a bevel gear 113, and a vehicle speed tuning shaft 115 disposed substantially in front of the shaft 114. A one-way clutch 120 for transmitting the vehicle speed tuning rotational force of the tuning input shaft 112 is installed on the tuning input shaft 112 while supporting the power from the vehicle speed tuning pulley 93 in one direction. When transmitted to the gear 117 by the clutch 120, the vehicle speed tuning shaft 115 is configured to rotate through the gear 117 and the reaping clutch 118 (see FIG. 14).

Further, a constant cutting speed clutch 122 for forming the constant cutting speed mechanism 121 and a high-speed cut gear 123 are installed on each of the shafts 114 and 115, and each of the shafts 114 and 115 is connected to the clutch 122 and the gear 1. When one of the gear clutches 118 and 122 is selectively engaged by the switching slider 124, the mowing unit 7 is driven at a drive speed synchronized with the vehicle speed. 7 is driven at a high-speed constant speed (high-speed cutting drive speed) faster than the vehicle speed synchronization speed to cut the lodging culm (see Fig. 14).

Further, the left end of the constant speed shaft 114 protrudes to the lower rear of the left side of the counter case 25, and the selection pulley 96 is supported on the left end of the constant speed shaft 114. On the other hand, the mowing transmission shaft 125 is pivotally supported at the lower front side on the left side of the counter case 25, and the right side of the mowing transmission shaft 125 is connected to the vehicle speed tuning shaft 115 via a torque limiter 126. The mowing transmission shaft 125 is projected to the left side of the counter case 25, and the mowing pulley 95 is pivotally supported at the left end of the mowing transmission shaft 125. A mowing drive shaft 127 is connected to the mowing input shaft 102 by a gear 128, and the mowing input pulley 103 is supported by the mowing drive shaft 127 (see FIG. 14).

[0061] Therefore, by turning on / off the vehicle speed tuning input to be transmitted to the torque limiter 126 and turning on / off the constant speed driving input by the same slider 124, the vehicle speed tuning input and the constant speed driving transmitted to the torque limiter 126 are performed. Eliminating the problem of simultaneous inputting, the vehicle speed tuning input and the constant speed driving input are selected and transmitted by the slider 124, and the transmission switching control becomes unnecessary, thus improving handling. .

[0062] On the other hand, the case of the gear 128 is installed on the left support base 23 via the fulcrum shaft 199 so as to be rotatable around the vertical axis, and the left side of the reaping input case 101 is fixed to the case of the gear 128. By being installed in each case 101, the mowing transmission shaft 130 can be inserted into the mowing frame 12 on the right end side of the case 101, and mowing power is input from the left end side of the mowing input shaft 102 to drive the mowing unit 7. Can be performed via the reaping transmission shaft 130, while the reaping unit 7 can be rotated about the fulcrum shaft 129 to the left side of the machine substantially horizontally to perform maintenance and the like around the respective cases 22 and 25 inside the machine.

As shown in FIGS. 9 and 14, the feed chain input shaft 107 is pivotally supported on the upper left side of the counter case 25. The input shaft 107 is connected to a feed chain drive shaft 132 via a feed chain clutch 131 by a chain 133 to transmit the rotation of the constant speed shaft 114 by changing the rotation speed of the vehicle speed tuning shaft 115. Install the feed chain transmission mechanism 134.

[0064] The feed chain mechanism 134 includes a sun gear 135, a planetary gear 136, and a ring gear 137. The planetary gear mechanism 138 is provided so as to be capable of continuously variable transmission. The sun gear 135 is engaged with the constant speed shaft 114, and the ring gear 137 is idlely supported on the constant speed shaft 114. The ring gear 137 is connected to the vehicle speed tuning shaft 115 via the gear 139 (see FIG. 14). .

On the other hand, the planetary gear 136 is idlely supported by the bearing body 140, and the bearing body 140 is idlely supported by the constant speed shaft 114, and the bearing body 140 is fed through the feed chain clutch 131 and the gear 141. By connecting to the chain drive shaft 132, the minimum rotation required to transport the grain culm is secured, and the speed of the feed chain 5 can be changed from a low constant rotation to a high rotation by synchronizing with the vehicle speed ( See Figure 14).

Further, a hydraulic cutting constant speed cylinder 143 for operating the switching slider 124 and a hydraulic threshing cylinder 144 for receiving the threshing clutch 97 are provided with an oil passage base, which is a top cover of the counter case 25. Fix to 145. On the other hand, there is provided a vehicle speed constant speed cylinder 146 for engaging the vehicle speed constant speed clutch 76, and a vehicle speed constant speed valve 147 for operating the vehicle speed constant speed cylinder 146; a cutting constant speed valve 149 for operating the cutting constant speed cylinder 143; A threshing valve 150 for operating the threshing cylinder 144 is hydraulically connected in parallel to the charge pump 78 (see FIG. 12).

Next, with reference to FIGS. 15 and 16, a description will be given of a configuration in which a mowing transmission mechanism 151 for switching the driving speed of the mowing unit 7 is installed in the counter case 25. FIG. The specification is such that the counter case 25 having the same shape as the counter case 25 in FIG. 13 without the cutting speed change mechanism 151 is used, and the cutting speed change mechanism 151 is provided. The low-speed gear 152 and the high-speed gear 153 forming the cutting speed change mechanism 151 are disposed between the tuning input shaft 112 and the cutting speed change shaft 154. A cutting speed slider 155 for performing low speed, neutral and high speed cutting speeds is provided, and one of the gears 152, 153 is selectively engaged with the cutting speed shaft 154 via the cutting speed slider 155. Then, the cutting speed output is transmitted to the vehicle speed tuning shaft 115 connecting the cutting speed change shaft 154 on the same shaft center.

On the other hand, a high-speed cut gear 156 is provided, and an inflow gear 123 and a high-speed cut gear 156 for forming the constant cutting speed mechanism 121 are installed between the shafts 114 and 115. A switching slider 124 for driving the mowing unit 7 at a low constant speed (flow driving speed) or a high constant speed (high cutting driving speed) is provided. When engaged with the shafts 114 and 115 alternatively, the mowing unit 7 is driven at a constant low speed (pour-in), and the culm of the mowing unit 7 is rotated at a constant rotational speed regardless of the vehicle speed. Will be transported to On the other hand, the mowing unit 7 is driven at a high speed constant (high-speed cut), and the mowing unit 7 is driven at a constant rotational speed higher than the vehicle speed synchronizing speed to cut the lodging grain (see FIG. 16).

Next, with reference to FIG. 13, FIG. 14, and FIG. 17 to FIG. 20, the mounting configuration of the torque limiter 126 installed on the cutting power transmission shaft 125 will be described. A torque limiter mounting hole 157 is formed in a detachable detachable case 25a for forming a part of the side wall of the counter case 25. A bearing cover 158 is fitted into the mounting hole 157 from the outside, and the bearing cover 158 is detachably fastened to the separation case 25a by a bolt 159. The intermediate portion of the reaping transmission shaft 125 is rotatably and slidably supported via a bearing bearing 160 on a removable bearing cover 158 for forming a part of the counter case 25.

On the other hand, the cutting power transmission shaft 125 is projected outside the counter case 25, and the cutting pulley 95 is fixed to one end side of the cutting power transmission shaft 125 by key fitting. The cutting power transmission shaft 125 is inserted into the inside of the counter case 25, and the flat gear type limiter transmission gear 161 is rotatably supported on the other end side of the cutting power transmission shaft 125 via a bearing 162. If the outer diameter of the pulley 95 is made larger than the outer diameter of the bearing lid 158, the bearing lid 158 and the bolt 159 can be attached and detached while the pulley 95 is removed from the shaft 125 (see FIG. 18).

On the other hand, if the outer diameter of the gear 161 is formed smaller than the mounting hole 157, the shaft 125 and the fitting portion of the bearing cover 158 enter and leave the mounting hole 157 while the gear 161 is mounted on the shaft 125. You can do that (see Figure 18). A flat gear 163 for engaging the gear 161 is engaged with the vehicle speed tuning shaft 115 so as to be engaged, and the limiter transmission gear 161 is connected to the vehicle speed tuning shaft 115 (see FIG. 16).

Next, the torque limiter 126 includes a cylindrical outer case 164 integrally formed on the side surface of the limiter transmission gear 161, a donut plate-shaped receiving plate 165 and a push plate 166 opposed to each other on the cutting transmission shaft 125. A donut plate-shaped torque plate 168 for arranging a plurality of torque rollers 167 on the same circumference at substantially equal intervals, and the torque rollers 167 of the torque plate 168 are arranged on opposite sides of the cutting transmission shaft 125 in the axial direction. A donut flat inner plate 169 and an outer plate 170 to be clamped from each other, and a detachable detachable screw screwed onto the transmission shaft 125 and pressed against the push plate 166 It has a nut 171 and a washer 172 (see FIG. 19). It should be noted that the outer case 164 of the main body of the torque limiter 126 is disposed inside the counter case 25 so that the outer case 164 and the like are oil-bathed.

As shown in FIGS. 18 and 19, the cutting transmission shaft 125 is supported by the bearing cover 158, the limiter transmission gear 161 is supported by the cutting transmission shaft 125 so as to be able to be pulled out, and the receiving plate 165 is supported by the outer case 16. 4, the inner plate 169, the torque plate 168, and the outer plate 170 are inserted into the outer case 164, and the inner hole of the inner plate 169 is engaged with the spline of the cutting transmission shaft 125. .

On the other hand, the protruding keys 175 on the outer periphery of the outer plate 170 are engaged with the key grooves 174 of the outer case 164 provided at approximately 120-degree intervals. When the torque spring 176 is supported by the seat plate 177, the seat plate 177 is rotatably supported on the outer end of the mowing transmission shaft 125, and the torque nut 178 is screwed onto the shaft 125, the torque limiter 126 Will be assembled in a unit structure with the bearing lid 158 and the mowing transmission shaft 125. Tighten the torque nut 178 to adjust the force of the tonnolek spring 176 to form the transmission torque of the torque roller 167 (see FIG. 18).

On the other hand, the cutting pulley 95 and the pulley boss 179 are separately formed, and the pulley 95 and the pulley boss 179 are detachably connected to each other with a bonoreto 180, and the pulley boss 179 is connected to the (J-take transmission shaft 125). Then, the torque nut 178 and the spring 176 are arranged outside the counter case 25 so that the torque spring 176 is pressed into contact with the outer surface of the pulley boss 179 (see FIG. 18).

[0076] An L-shaped oil hole 181 is formed in the shaft core of the mowing transmission shaft 125, one end of the oil hole 181 is opened to the end face of the shaft 125 in the counter case 25, and the other end of the oil hole 181 is opened. Is opened on the peripheral surface of the mowing transmission shaft 125, the centrifugal force generated by the rotation of the mowing transmission shaft 125 causes the oil in the counter case 25 to move from the oil hole 181 toward the torque roller 167, and this oil is removed. It will be forcibly lubricated by being forcibly sent to the torque roller 167 by centrifugal force (see Fig. 17).

On the other hand, a rectangular supporting hole 182 similar to the columnar shape of the torque roller 167 in a plan view is formed in the torque plate 168. A torque roller 167 is rotatably contained in the support hole 182. A pair of tongue pieces 183 are formed opposite to the opening edge on the long side of the support hole 182 facing each other, and the tongue pieces 183 are formed so as to be in sliding contact with the outer periphery of the torque roller 167 (see FIG. 19).

[0078] Further, a bent edge 184 is formed on the outer periphery of the torque plate 168, and the tongue piece 183 is formed in the same shape as the bent edge 184. When the torque plate 168 is formed so as to protrude in one direction and the thickness (width in the axial direction) of the torque plate 168 is formed smaller than the outer diameter of the torque roller 167, the outer peripheral side of the torque roller 167 projects on both side surfaces of the tonolek plate 168, The torque roller 167 comes into sliding contact with the inner plate 169 and the outer plate 170 (see FIG. 19). When the distal ends of the pair of tongue pieces 183 for forming the holder are bent in the circumferential direction of the torque roller 167, the outer circumference of the torque roller 167 is rotatably held by the pair of tongue pieces 183. (See Figure 20).

[0079] Note that, with respect to the radiation passing through the center of rotation of the torque plate 168, the torque roller 167 is tilted toward the lower rotation side of the torque plate 168 at a constant inclination angle with respect to the radiation passing through the rotation center of the torque plate 168. Is placed on the Tonoreq board 168. Rolling shaft core force of torque roller 167 Torque roller 167 is arranged on torque plate 168 so as to be inclined by a certain angle with respect to a plane (radiation) including the rotation center of torque plate 168, and flatness of vehicle speed tuning shaft 115 is set. When the outer case 164 is rotationally driven via the gear 163, each torque roller 167 rolls while contacting the inner plate 169 and the outer plate 170, and the torque plate 168 also rotates.

At this time, each of the torque rollers 167 tries to roll in a direction inclined by a certain angle with respect to the rotation trajectory of the outer plate 170, while the rotation trajectory of the outer plate 170 is regulated by the torque plate 168. , A frictional resistance proportional to the pressure of the torque panel 176 is generated.

Furthermore, since each torque roller 167 generates sliding friction while rolling, static friction does not occur, and a stable frictional resistance force due to dynamic friction is always obtained. On the other hand, when the mowing drive load on the mowing drive shaft 125 increases, or when the rotation speed of the outer case 164 suddenly changes to the high speed side due to a change in the input speed on the spur gear 163 side, the inner plate 169 and the outer plate 1 Each rotational torque difference of 70 increases, and each rotational torque difference becomes larger than the frictional resistance of the torque roller 167. At this time, the inner plate 169 and the outer plate 170 slide with respect to the torque roller 167, and the transmission power is cut off.

[0082] As described above, one of the hydraulic transmission mechanism 40 and the constant speed mechanism 121 is configured to transmit the driving force to the reaping unit 7, which is a working unit. The torque limiter 126 is disposed on the cutting power transmission shaft 125 for rotating the cutting unit 7. Even if a shock occurs due to the drive torque difference when switching between the hydraulic transmission mechanism 40 and the constant speed mechanism 121, the shock is absorbed by the torque limiter 126. You can do it. On the other hand, the hydraulic oil level in the counter case 25 for installing the torque limiter 126 inside is higher than the installation position of the shaft 125 of the torque limiter 126, so that the hydraulic oil power is sufficiently supplied to the torque limiter 126. Being lubricated.

[0083] On the other hand, when the tonnole nut 178 and the tonneau nut 176 are installed outside the pulley boss 179, the torque limiter 126 can be torque-set by an external force, thereby improving handling such as maintenance. When the cutting pulley 95 and the pulley boss 179 are formed separately and the cutting pulley 95 and the pulley boss 179 are compacted by the bonnet 180, the cutting pulley 95 can be removed with the pulley boss 179 attached, and the torque can be reduced. With the set torque of the limiter 126 being kept constant, the belt can be replaced by removing the cutting pulley 95.

Further, as shown in FIGS. 19 and 20, the receiving plate 165 and the pressing plate 166 are opposed on the rotating shaft 125. A plurality of sets of inner plates 169, tonolek plates 168, and outer plates 170 are provided between the receiving plate 165 and the pressing plate 166. The inner plate 169 is engaged with the rotating shaft 125, the outer plate 170 is engaged with the outer case 164, and the torque roller 167 is disposed on the torque plate 168. On the other hand, the torque nut 178 is screwed onto the rotating shaft 125, the spring seat plate 177 is locked on the torque nut 178, and the spring 176 is arranged between the spring seat plate 177 and the pressing plate 166. The receiving plate 165 or the pressing plate 166 is formed so as to face the pressure receiving surfaces 185, 186 and the torque plate 168. The pressure receiving surfaces 185 and 186 are formed in a substantially concave shape so that the pressure receiving surfaces 185 and 186 of the receiving plate 165 or the pressing plate 166 are radially flat by the pressing force for generating the set torque.

[0085] Each of the pressure receiving surfaces 185 and 186 of the receiving plate 165 and the pressing plate 166 has a tapered structure having the inclination angles Al and A2. Each of the pressure receiving surfaces 185 and 186 is formed as a taper having the inclination angles Al and A2 so that the outer peripheral sides of the receiving plate 165 and the pressing plate 166 come into contact with the inner plate 169 first (see FIG. 20).

[0086] Accordingly, since the receiving plate 165 or the pressing plate 166 is deflected by the pressing force when the set torque is generated, and the pressure receiving surfaces 185 and 186 become substantially flat, the smoothed surface pressure is applied to the tonnole roller 167 surface. As a result, the uneven wear of the torque roller 167 can be reduced, the durability can be improved, and the transmission accuracy of the set torque can be improved. Further, even when the thickness of the receiving plate 165 or the pressing plate 166 is not formed so thick as not to be distorted by the set torque, a space-saving and compact device that can smooth the surface pressure of the pressure receiving surfaces 185 and 186. The unit can be configured.

[0087] Further, as shown in Figs. 17 and 20, a step portion 187 is provided on the receiving plate 165, and the step portion 187 is connected to a bearing. The bearing 162 is formed so as to receive the set torque by contacting the inner part 188 of the bearing 162. Further, when the step 189 is provided on the push plate 166 and the step 189 is brought into contact with the washer 172, the circumference of the push plate 166 is fixed between the washer 172 fixed with the nut 171 and the push plate 166. By forming the space on the side, the tightening force of the nut 171 acts on the push plate 166 from the step portion 189 via the washer 172 in a straight line.

As shown in FIG. 17, when a shaft cover 191 made of synthetic resin is fixed to a pulley boss 179 with a screw 190 and a torque spring 176 and a torque nut 178 are provided inside the shaft cover 191, the shaft cover With the 191 removed, the torque nut 178 can be operated from the outside of the counter case 25, and the set torque of the torque limiter 126 can be adjusted. Also, when oil holes 181 are respectively opened at a plurality of locations on the outer periphery of the rotating shaft 125 in correspondence with the gaps between the plurality of inner plates 169, the oil force from each oil hole 181 to the keyway of the outer case 164 It moves to the outside of the gear case 164 through the 174 by centrifugal force, and the torque roller 167 can be forcibly lubricated.

As is apparent from the above, when the oil holes 181 are formed so as to be able to supply oil by respectively opening a plurality of closing portions partitioned by the inner plate 169, the inner plate 169, the outer plate 170, and the torque plate Even if the 168s are provided in multiple layers, the lubricating oil can be sufficiently supplied to the torque roller 167, the transmission torque can be properly maintained, the durability can be improved, and the function of the torque limiter 126 can be improved.

When the oil in the closing portion is discharged from the key groove 174 of the outer case 164 that engages the outer plate 170, the oil around the torque roller 167 can be efficiently discharged from the key groove 174 by centrifugal force. Thus, the supply of oil to the torque roller 167 can be promoted, and the torque roller 167 can be efficiently lubricated. On the other hand, when a space is formed on the circumferential side of the push plate 166 between the washer 172 and the push plate 166, the tightening force of the nut 171 directly acts on the push plate 166 via the washer 172, and The pressure receiving surface 186 of the plate 166 is smoothed to prevent an uneven load on the torque roller 167.

[0091] Further, as shown in Figs. 1 to 4 and 9, a column controller 192 installed in the cabin 18 behind the driver's seat 20 and a front plate 193 of the left and right support bases 23 and 24 are installed. Running controller 194, the engine controller 195 installed on the cabin frame 30 outside the engine room cover 31, and the threshing section 4 installed on the rear of the grain tank 15 threshing section And a roller 196. The controllers 192, 194, 195, and 196 are configured to be connected by can communication.

[0092] On the other hand, a hydraulic valve set 197 for raising and lowering the reaping unit 7, controlling the level of the machine, and moving the discharge auger 17 is installed on the upper surface of the machine base 3 below the grain tank 15 (see Fig. 5). . It has an outside air introduction cover 198 arranged outside the engine room cover 31 and a grain tank 15 that is horizontally rotated around a vertical discharge auger 16. The grain tank 15 and the outside air introduction power bar 198 are installed rotatably to the side of the fuselage (see Fig. 3). A storage case 200 for installing a part of the gear 128 therein is installed on the upper part of the left support base 23 via a fulcrum shaft 199 so as to be rotatable around the vertical axis (see FIG. 4). The storage case 200 is arranged on the left side of the cutting input case 101 for supporting the cutting frame 12. A part of the gear 128 is provided inside the reaping input case 101 (see FIG. 10). The driving force of the mowing unit 7 is inputted from the left end side of the mowing input shaft 102 and transmitted to the mowing transmission shaft 130 inserted in the mowing frame 12. On the other hand, when the mowing part 7 is rotated sideways around the fulcrum shaft 199 substantially horizontally toward the left side of the machine, maintenance and the like of the respective cases 22, 25 inside the machine can be performed.

[0093] Further, as shown in Figs. 13 and 15, a counter case 25 is provided to the transmission case 22 for driving the traveling crawler 2, the mowing unit 7 and the threshing unit 4, and the power from the engine 21. In the combine transmitted through the cutter, the specification shown in FIG. 15 provided with a cutting speed change mechanism 150 for changing the driving speed of the cutting unit 7 and the specification shown in FIG. In the case of using the counter case 25, the counter case 25 can be used for a plurality of different specifications, and the manufacturing cost can be reduced.

[0094] When the driving speed of the mowing unit 7 is switched from the vehicle speed synchronizing speed to the constant driving speed (flow-in speed) and the mowing unit 7 is driven, the specification shown in FIG. By increasing the constant driving speed (inflow speed) of the mowing unit 7 when the specification of FIG. 13 without the mowing transmission mechanism 150 is adopted, compared to the constant driving speed of the mowing unit 7 at the time of Can be driven corresponding to a high vehicle speed.

Further, in the specification of FIG. 15 in which the cutting speed change mechanism 150 for changing the driving speed of the cutting unit 7 is provided, the flowing gear 123 as a flowing mechanism and the high-speed cutting gear 156 as a high-speed cutting mechanism are used. Install it in counter case 25. On the other hand, Fig. 1 without the mowing transmission mechanism 150 In the specifications of 3, the high-speed cut gear 156 is removed to replace the inflow gear 123 and the shaft 154, and the cutting speed change mechanism 150 is provided, and the specification of FIG. 15 without the cutting speed change mechanism 150 is provided. And the manufacturing cost can be reduced.

On the other hand, since the installation position force S of the travel controller 194 and the cutting section 7 are released by the lateral rotation, the travel controller 194 is operated inside the body away from the engine 21 and maintenance work is performed. It can be installed at a position that is easy and close to the counter case 25. The harness for extending between the traveling controller 194 and the counter case 25 can shorten the extension distance, improve the assembling and handling properties, and reduce the manufacturing cost.

Further, as shown in FIGS. 5, 6, and 9, the fastening seat 201 is integrally formed with the counter case 25, and the receiving stands 202 and 203 are arranged on the upper surface of the machine base 3 and on the support base 23. Fix the fastening seat 201 to the cradle 202, 203 with the bolt 204. The counter case 25 is fixed to the machine base 3 and the support base 23. On the other hand, the battery 206 is formed so as to be able to enter and exit the support table 23 from the opening 205 on the side surface of the support table 23. For example, it is not necessary to install the battery 206 by extending the machine base 3 in front of the threshing unit 4 forward. Machine 3 can be used effectively and maintenance work can be simplified.

[0098] Further, since the hydraulic valve set 197 is provided on the machine base 3 on the lower surface of the grain tank 15 that can be rotated sideways, when the grain tank 15 is rotated sideways, the hydraulic valve Set 1 97 will be easier to maintain. On the other hand, since the exhaust pipe 208 of the engine 21 is provided below the threshing unit 4 between the counter case 25 on the front side of the machine 3 and the fuel tank 207 on the rear side of the machine 3, The exhaust pipe 208 can be installed apart from the 206 and the hydraulic valve set 197.

[0099] Further, as shown in Figs. 6 and 8, a counter case 25 is provided between the left and right support bases 23 and 24 and the threshing unit 4. A support frame 209 for connecting the left and right support bases 23 and 24 is horizontally mounted above the counter case 25. Since the left and right support bases 23 and 24 are connected by the support frame 209, the support frame 209 can be used as a mounting member of the harness 210 or a reinforcing member of the support base 23.

[0100] When the harness 210 of the transmission valve 211 is supported by the support frame 209, The support frame 209 can be used as the reinforcing member of the 23, and the harness 210 can be easily attached using the support frame 209. When the controller 194 of the transmission valve 211 is provided between the left and right support bases 23 and 24, and the lateral rotation fulcrum 199 of the mowing part 7 is provided on one of the support bases 23, the controller 194 is connected to the mowing part 7. By using the front portions of the support bases 23 and 24 that are opened by the lateral rotation of the support bases 23 and 24, the support bases 23 and 24 can be installed for easy maintenance, so that the counter case 25 and the controller 194 can be close to each other.

[0101] Further, when the bracket 212 is installed on the front side of the transmission case 22 and the bracket 212 is fixed in the middle of the connection frame 34 as shown in FIGS. Restrictions such as the mounting height of 34 or the height of the attached parts provided on the upper surface of the transmission case 22 can be relaxed, so that the structure and the body structure of the transmission case 22 can be simplified and the rigidity can be improved. In addition, when a drain hole 213 is provided on the upper surface of the transmission case 22 and an air vent pipe 214 is connected to the drain port 213, the drain air 213 can be installed at a substantially highest position on the upper surface of the transmission case 22, and the air vent pipe 214 can be installed. The connection allows the drain structure of the transmission case 22 to be simplified.

Further, as shown in FIG. 21, on the input side of a work controller 282 constituted by a microcomputer, a threshing switch 272 for detecting operation of a work lever 271 for driving the threshing unit 4 and a reaper The cutting switch 273 for detecting the operation of the working lever 271 for driving the section 7, the cutting gear switch 274 for switching the cutting gear slider 155 to the low speed side or the high speed side, and the high speed forward switching operation of the main gear lever 81. A high-speed operation switch 275 for detecting, a reverse switch 276 for detecting the reverse switching operation of the main shift lever 81, a manual pouring switch 278 for detecting the stepping operation of the pouring ditch 277, and a sub-speed switching (low speed or high speed). ), The automatic lift switch 280 that automatically raises or lowers the mowing part 7, and the discharge auger 17 from this storage position to the grain discharge position. An automatic set switch 281 for turning dynamically, left and right vehicle speed sensors 285 and 286 for detecting the vehicle speed of the left and right traveling crawlers 2, a grain culm sensor 287 for detecting the presence or absence of a transported grain culm in the mowing section 7, and a mowing section 7 And a cutting input sensor 288 for detecting, via a low-speed gear 152, an input rotation speed of a tuning input shaft 112 for inputting a vehicle speed tuning driving force to the vehicle.

As shown in FIG. 21, the output side of the work controller 282 is The cutting speed is changed to low speed 289, the cutting speed is changed to high speed, the cutting speed high speed solenoid 290, the feed chain clutch cylinder is operated to cut off the feed chain clutch 131, and the feed chain solenoid 291 is fixed. Is connected to a pouring solenoid 292 that engages the switching slider 124 with the pouring gear 123, and a high-speed cut solenoid 293 that operates the constant rotation cylinder to engage the switching slider 124 with the high-speed cutting gear 156. Further, as shown in FIG. 16, a rotation sensor 301 for detecting a rotation speed for calculating a cutting input rotation speed is installed on the tuning input shaft 112, and the rotation of the tuning input shaft 112 detected by the rotation sensor 301 is set. The mowing input rotational speed is calculated based on the number and the number of gear teeth. It should be noted that a rotation sensor 302 for detecting a rotation speed for calculating the cutting input rotation speed may be provided on the cutting transmission shaft 125 so that the cutting input rotation speed is calculated.

Next, FIG. 22 is a flowchart of the speed control of the cutting unit 7, and FIG. 23 is a cutting speed KVx (driving speed of the cutting unit 7) of the cutting transmission shaft 125 for driving the cutting unit 7, and a vehicle speed SV. FIG. 4 is a diagram showing the relationship between the two. Control for switching the driving speed of the mowing unit 7 will be described with reference to FIGS. When the cutting switch 273 is turned on (Slyes), the automatic lift switch 280 is turned on, and the cutting unit 7 is lowered to the grain culm cutting height (S2yes), the cutting rotation speed KVx of the cutting transmission shaft 125 is changed to the low speed constant speed rotation Vq. Is performed (S3). In the low speed constant speed control, the constant cutting speed cylinder 143 is operated by exciting the pouring solenoid 292. The switching slider 124 is switched by the constant cutting speed cylinder 143. The switching slider 124 is connected to the inflow gear 123. A constant low-speed rotational force for driving the reaping transmission shaft 125 is transmitted from the pouring gear 123 to the reaping transmission shaft 125. The reaping unit 7 is driven at a low speed constant speed rotation Vq.

On the other hand, when the low speed constant speed control (S3) is being performed, when the main shift lever 81 is operated by the operator to increase the vehicle speed SV and the harvesting operation is started, the vehicle speed is reduced. When the vehicle speed SV input from the sensors 285 and 286 is increased to the vehicle speed qH corresponding to the lower return point Dt2 (S4yes), the vehicle speed tuning speed control is performed (S5). In this vehicle speed tuning speed control, the constant cutting speed cylinder 143 operates so as to return the switching slider 124 to neutral. The vehicle speed tuning driving force output from the traveling motor 42 of the transmission case 22 is transmitted to the low-speed gear 152 or The signal is transmitted to the mowing transmission shaft 125 via the high-speed gear 153. The drive speed in the reaping unit 7 is switched to the vehicle speed synchronization speed in synchronization with the vehicle speed SV and in accordance with a vehicle speed synchronization pattern that increases in proportion to the increase in the vehicle speed SV.

When the vehicle speed tuning speed control (S5) is being performed, the main shift lever 81 is operated by the operator to reduce the vehicle speed SV, and the vehicle speed input from the vehicle speed sensors 285, 286 When the SV is reduced to the vehicle speed tH corresponding to the lower shift point Dt (S6yes), the low speed constant speed control for setting the rotation speed KVx of the reaping transmission shaft 125 to the low speed constant speed rotation Vq is performed (S7). The vehicle speed tH force S corresponding to the lower shift point Dt is the lower limit of the vehicle speed SV in the vehicle speed tuning section D. The rotation speed Vt of the mowing transmission shaft 125 corresponding to the lower shift point Dt is switched to the low speed constant speed rotation Vq corresponding to the lower constant speed point Dtl substantially the same as the lower return point Dt2.

[0107] When the low speed constant speed control (S7) is being performed, the grain stalks cut by the cutting unit 7 are carried out to the threshing unit 4, and the grain stalks detected by the grain stalk sensor 287 are removed by the cutting unit. When it is no longer from 7 (S8no), stop control for stopping the reaper 7 is performed (S9). With both the low speed cutting solenoid 289 and the high speed cutting solenoid 290 turned off, the low speed gear 152 or the high speed gear 153 is set to the neutral position, and the cutting unit 7 is stopped.

When the vehicle speed tuning speed control (S5) is being performed, the main shift lever 81 is operated by the operator to increase the vehicle speed SV, and the vehicle speed input from the vehicle speed sensors 285 and 286 is used. When the SV is increased to the vehicle speed rH corresponding to the upper shift point Dr (SlOyes), high-speed constant speed control is performed to set the cutting rotation speed KVx of the cutting transmission shaft 125 to a high-speed constant speed rotation Vrx (Sl l). In this high-speed constant speed control, the constant cutting speed cylinder 143 is operated by exciting the high-speed cut solenoid 293. The switching slider 124 is switched by the constant cutting speed cylinder 143. The switching slider 124 is connected to the high-speed cut gear 156. A high-speed constant-speed rotational force for driving the mowing transmission shaft 125 is transmitted from the high-speed cut gear 156 to the mowing transmission shaft 125. The speed rotation Vr of the reaper 7 corresponding to the upper transition point Dr is switched to the high speed constant speed rotation Vrx corresponding to the first upper constant speed point Drl, and the reaper 7 is driven by the high speed constant speed rotation Vrx. Will be. The vehicle speed rH corresponding to the upper shift point Dr becomes the upper limit of the vehicle speed SV in the vehicle speed tuning section D.

[0109] On the other hand, when the high-speed constant speed control (S11) is being performed, the main shift lever 81 is operated. When the vehicle speed SV is operated to slow down the vehicle speed SV and the vehicle speed SV input from the vehicle speed sensors 285 and 286 is reduced to the vehicle speed pH corresponding to the upper return point Dr3 (S12yes), the vehicle speed tuning speed control is performed. (S5). In this vehicle speed tuning speed control, the constant cutting speed cylinder 143 operates so as to return the switching slider 124 to the neutral position. The vehicle speed synchronizing driving force output from the traveling motor 42 of the transmission case 22 is transmitted to the mowing transmission shaft 125 via the low speed gear 152 or the high speed gear 153. The drive speed in the mowing unit 7 is switched from the high-speed constant speed rotation Vrx corresponding to the second upper constant speed point Dr2 to the vehicle speed synchronization speed rotation Vry corresponding to the upper return point Dr3, in synchronization with the vehicle speed SV and increasing the vehicle speed SV. The vehicle speed is switched to the vehicle speed tuning speed along the vehicle speed tuning pattern which increases in proportion to the vehicle speed.

[0110] As shown in Figs. 23 and 24, a vehicle speed tuning section D to be transmitted to the mowing transmission shaft 125 via the high-speed gear 153 is formed. A vehicle speed tuning section E to be transmitted to the mowing transmission shaft 125 via the low-speed gear 152 is formed. In the vehicle speed tuning sections D and E, the upper and lower limits of the vehicle speed SV are different from each other. On the other hand, the range of the vehicle speed tuning speed (Vr-Vt) corresponding to the vehicle speed SV in each vehicle speed tuning section D and E, the constant low speed Vq of the reaper 7 and the constant high speed Vrx of the reaper 7 are the same. Values.

[0111] As is clear from the above, the drive speed KVx in the reaper 7 is adjusted to the vehicle speed tuning speed according to the vehicle speed tuning pattern which is synchronized with the vehicle speed SV and increases in proportion to the increase of the vehicle speed SV, or to the increase or decrease of the vehicle speed SV. Regardless of the combine, which is configured to drive the reaping unit 7 by switching to one of the preset substantially constant rotational speeds Vq and Vrx, the vehicle speed sensors 285 and 286 for detecting the vehicle speed SV, and the reaping unit A cutting input sensor 288 for detecting the number of rotations of the input shaft 112 for driving the driving shaft 7, and a driving speed KVx of the cutting unit 7 is set to one of a low constant speed Vq, a vehicle speed tuning speed, or a high constant speed Vrx. When the vehicle speed SV in the vehicle speed tuning section D is reduced to the lower shift point Dt, the drive speed KVx of the reaper 7 is switched to the constant low speed Vq while the work controller 282 is a control means for switching. Vehicle speed When the SV increases to the upper shift point Dr, the drive speed KVx of the reaper 7 is controlled to be switched to the high-speed constant speed Vrx.

[0112] Therefore, when the vehicle speed SV in the vehicle speed tuning section D is reduced near the lower shift point D, the drive speed KVx of the reaper 7 is switched to the low-speed constant speed Vq. By determining the vehicle speed tH of the lower dislocation point Dt so that the portion 7 can be driven at a vehicle speed synchronization speed lower than the low speed constant speed Vq, the grain culm raising operation of the cutting unit 7 in the low speed traveling harvesting operation is performed. It is possible to prevent the culm's ear from being handled and shedding.

On the other hand, when the vehicle speed SV is increased to the upper shift point Dr, the driving speed K Vx of the reaper 7 is controlled to be switched to the high-speed constant speed Vrx. By determining the vehicle speed rH of the upper shift point Dr so that the vehicle can be driven at the high speed constant speed Vrx higher than the speed tuning speed, it is possible to prevent an overload in the high speed running harvesting operation.

Therefore, the harvester 7 can be properly driven at the low-speed constant speed Vq or the high-speed constant speed Vrx in any of the low-speed traveling harvesting operation and the high-speed traveling harvesting operation. Workability can be improved, and work efficiency of high-speed traveling harvesting can be improved.

[0115] Since the low constant speed Vq is set higher than the drive speed KVx of the reaping unit 7 corresponding to when the vehicle speed SV is the lower shift point Dt, the reaping is performed. When the vehicle 7 is driven at a vehicle speed tuning speed according to the vehicle speed tuning pattern, the vehicle speed in the vehicle speed tuning section is shifted to the lower shift point so that the driving speed KVx of the reaper 7 becomes lower than the low speed constant speed Vq. Even if the speed is temporarily reduced to near Dt, the driving speed KV X of the cutting unit 7 is maintained at the vehicle speed synchronization speed according to the vehicle speed synchronization pattern, and the tip of the grain culm is handled by the raising operation of the cutting unit. To prevent shedding.

When the vehicle speed SV is increased by an appropriate value from the lower shift point Dt as appropriate, the drive speed KVx force of the reaper 7 once at the low speed constant speed Vq reaches the lower return point Dt2 on the vehicle speed tuning pattern. After the return, the control means 282 switches so as to adopt the vehicle speed tuning speed on the vehicle speed tuning pattern as the driving speed KVx, so that the vehicle speed qH of the lower return point Dt2 is changed to the lower shift point Dt. By making the vehicle speed tH faster than the vehicle speed tH, the drive speed KVx of the reaper 7 can be smoothly switched from the low-speed constant speed Vq to the vehicle speed tuning speed along the vehicle speed tuning pattern.

[0117] The high-speed constant speed Vrx is set to be higher than the drive speed KVx of the reaper 7 corresponding to the case where the vehicle speed SV in the vehicle speed tuning section D is the upper shift point Dr. Therefore, the drive speed KVx of the mowing unit 7 can be switched from the vehicle speed tuning speed according to the vehicle speed tuning pattern to the high-speed constant speed Vrx with a margin in the output of the engine 21. When the mowing unit 7 is driven at a vehicle speed tuning speed according to a vehicle speed tuning pattern, the harvesting unit 7 can be smoothly shifted to a high-speed running harvesting operation in which the mowing unit 7 is driven at the high-speed constant speed Vrx. Work efficiency can be improved.

When the vehicle speed SV is decelerated by an appropriate value from the upper shift point Dr, the drive speed KVx force of the reaper 7 once at the high speed constant speed Vrx reaches the upper return point Dr3 on the vehicle speed tuning pattern. After returning, the control means 282 switches so as to adopt the vehicle speed tuning speed on the vehicle speed tuning pattern as the driving speed KVx, so that the vehicle speed pH at the upper return point Dr3 is changed to the upper shift point. By making the vehicle speed rH slower than Dr's vehicle speed rH, the drive speed KVx of the reaper 7 can be smoothly switched from the vehicle speed tuning speed along the vehicle speed tuning pattern to the high-speed constant speed.

[0119] The control means 282 controls the driving speed KVx of the reaper 7 so as to switch from the vehicle speed tuning speed to the low speed constant speed Vq when the vehicle moves backward. When the vehicle is traveling in reverse, the mowing unit 7 is in a stopped state. Therefore, even if the mowing unit 7 is stopped and driven from the off state, the driving of the mowing unit 7 is started at a constant low speed Vq. Accordingly, it is possible to suppress the impact load when the driving of the mowing unit 7 is started.

Next, information display and control by CAN communication will be described with reference to FIGS. 25 to 27. As shown in FIG. 25, the work controller 282 in FIG. 21 includes a column controller 350 and a travel controller 351. The engine controller 352 for controlling the engine 21, the column controller 350, and the travel controller 351 are connected by a CAN cable 353. Note that a cutting position sensor 354 for detecting the position at which the cutting unit 7 is moved up and down is arranged on the input side of the travel controller 351.

On the other hand, to the output side of the column controller 350, a total display liquid crystal panel 355 arranged on the driving operation handle 19 is connected. On the input side of the column controller 350, a first selection switch 356 and a second selection switch 357 for switching the display content of the liquid crystal panel 355, and a first selection switch 356 and a second selection switch 357 are selected. The setting switch 358 and the determination switch 359 for determining the display content of the liquid crystal panel 355 are And connect them.

As shown in FIG. 26, by operating the first selection switch 356, the second selection switch 357, and the setting switch 358 to switch the display content of the liquid crystal panel 355 to an error display, an error code (for example, CO-320), error location (eg, engine oil temperature sensor, engine room, engine controller) and force LCD panel 355 displays.

Next, as shown in FIG. 27, by operating the first selection switch 356, the second selection switch 357, and the setting switch 358 to switch the display content of the liquid crystal panel 355 to a failure check, The error code (eg, CO-320), the error location (eg, rack position sensor, engine room, engine controller), the error occurrence time (eg, 1234h) and the force are displayed on the liquid crystal panel 355.

On the other hand, as shown in the flowchart of FIG. 28, the mowing unit 7 is operated at a low constant speed (pour), a high constant speed (high cut) speed, or a vehicle speed tuning speed. A constant rotating force is transmitted to the motor shaft 46 of the traveling motor 39 of the hydraulic traveling transmission member 40, and the traveling crawler 2 is directly driven at a higher rotation than the output of the motor 39.

When the high-speed operation switch 275 is turned on while the automatic switch 284 is on, the high-speed operation solenoid 295 for engaging the bypass clutch and the sub-transmission switch 279 are switched. A threshing clutch solenoid 297 for driving the sub-transmission cylinder to set the traveling motor 39 to low speed or high speed output, and a threshing clutch solenoid 297 for turning on the threshing switch 97 when the threshing switch 272 is turned on; The cutting lift solenoid 298 for raising or lowering the lifting cylinder 11 by turning on the automatic lift switch 280 and the discharge auger 17 to the grain discharge position or the machine storage position by turning on the automatic set switch 281 described above. A discharge motor 299 for movement is connected to the work controller 282.

[0126] As described above, the pouring pedal 277, which is a pouring operation member that performs a pouring operation for carrying out the culm of the mowing unit 7 to the threshing unit 4, is provided, and the mowing unit 7 that operates in synchronization with the vehicle speed is tuned. In a combine drive driven at a rotation speed different from the rotation speed, a pouring operation for pouring the reaping unit 7 based on the rotation speed of the drive input of the reaping unit 7 when the pouring pedal 277 is operated. The gear 123 and the high-speed cut gear 156 are selected, and the number of rotations of the drive input of the reaper 7 is selected. And using the pouring gear 123 This eliminates the problem that the driving speed of the reaper 7 at the time of starting the pouring operation is largely changed, and allows the pouring operation to be performed using the high-speed cut gear 156 without causing the operator to feel uncomfortable.

Further, a cutting input sensor 288 for detecting the number of rotations of the drive input of the vehicle speed tuning of the reaper 7 is provided, and when the pouring pedal 277 is operated, the input speed of the vehicle speed tuning of the reaper 7 is controlled by the pouring gear 123. When the rotational speed is equal to or lower than the pouring rotation speed (the rotational speed is lower than a certain rotational speed lower than the pouring rotational speed), the pouring solenoid 292 is turned on, and the pouring rotational power is continued via the pouring gear 123.

On the other hand, when the rotation speed of the mowing unit 7 is equal to or higher than the rotation speed of the pouring gear 123 (or higher than a certain rotation speed higher than the pouring rotation speed), the high-speed cut solenoid 293 is turned on and the high-speed cut gear 156 is turned on. By continuing the high-speed rotation power and setting the flow rotation power by the flow gear 123 to the low speed side, the operation of the flow gear 123 can be started smoothly with a smaller speed difference than before, and under high-speed cutting conditions. Even if it does, the mowing unit 7 is operated at the highest speed by the pouring operation by the high-speed gear 156, so that the conventional feeling that the mowing speed is reduced is eliminated.

[0129] Further, a tuning input shaft 112, which is a drive system for vehicle speed tuning, a pouring gear 123, which is a drive system for pouring, and a high-speed, constant-speed rotational drive system for constant rotation on the high-speed side. One of the high-speed cut gears 156 is selected to drive the mowing unit 7, and the mowing unit 7 is rotated at a constant speed to perform the mowing operation. The structure is simplified and the mowing drive performance is improved.

On the other hand, a mowing transmission mechanism 151 is provided on the input path of the tuning input shaft 112 for driving the mowing unit 7, the power transmission is stopped by maintaining the mowing transmission mechanism 151 at neutral, and the mowing unit 7 is moved to each of the gears. When the pouring operation is performed via one of 123 and 156, the mowing transmission mechanism 151 is also used as a mowing clutch to turn on and off the driving force synchronized with the vehicle speed, and when the pouring operation is performed, the motor shaft 46 of the traveling motor 39 is used. The driving force loss of the traveling crawler 2 is reduced, the cutting drive structure is simplified, and the driving efficiency of the traveling crawler 2 is improved.

[0131] As shown in the flowchart of Fig. 28 and the output diagram of Fig. 29, a description will be given of high-speed cut control in which the mowing unit 7 is rotated at a constant speed higher than the vehicle speed tuning speed. High speed reaping shift In this case, if the vehicle speed SV is equal to or higher than the vehicle speed a during the vehicle speed synchronization control, high-speed constant rotation control is performed in which the reaper 7 is rotated at a constant speed higher than the vehicle speed synchronization speed. On the other hand, when the vehicle speed SV is not higher than the vehicle speed a, the vehicle speed tuning control is performed.

[0132] On the other hand, when the harvesting shift is at a high speed, the vehicle speed synchronization control is not being performed, and when the vehicle speed SV is less than the vehicle speed b, the vehicle speed synchronization control is performed. On the other hand, when the vehicle speed SV is not lower than the vehicle speed b, high-speed constant rotation control is performed in which the mowing unit 7 is rotated at a constant speed higher than the vehicle speed synchronization speed.

[0133] When the harvesting shift is not at a high speed, the vehicle speed tuning control is being performed, and when the vehicle speed SV is equal to or higher than the vehicle speed c, high-speed constant rotation control is performed in which the cutting unit 7 is rotated at a constant speed higher than the vehicle speed tuning speed. Will be. On the other hand, when the vehicle speed SV is not higher than the vehicle speed c, the vehicle speed tuning control is performed.

On the other hand, when the harvesting shift is not at a high speed, the vehicle speed synchronization control is not being performed, and when the vehicle speed SV is less than the vehicle speed d, the vehicle speed synchronization control is performed. On the other hand, when the vehicle speed SV is not lower than the vehicle speed d, high-speed constant rotation control is performed in which the driving speed of the reaping unit 7 is constantly rotated at a higher speed than the vehicle speed synchronization speed.

[0135] As shown in the flowchart of Fig. 30 and the output diagram of Fig. 31, a description will be given of the reaping quick control for rotating the reaping unit 7 at a constant speed according to the present invention described in the claims. When the pouring switch 278 is turned on by stepping on the pouring pedal 277 which is a reaping quick pedal, the reaping section is operated when the vehicle is moving forward, the cutting speed is high, and the vehicle speed SV is equal to or higher than the vehicle speed a. The harvesting quick “high” control, in which the drive speed of 7 is driven at a constant speed on the high speed side of the vehicle speed tuning speed or higher, is performed. On the other hand, when the vehicle speed SV is not equal to or higher than the vehicle speed a, the harvesting quick “low” control is performed in which the driving speed of the mowing unit 7 is driven to rotate at a constant speed at a low speed side of the vehicle speed tuning speed or lower.

On the other hand, when the vehicle is moving forward and the harvesting speed is not high, if the vehicle speed SV is equal to or higher than the vehicle speed b, the driving speed of the mowing unit 7 is kept constant at a high speed side of the vehicle speed tuning speed or higher. Driving mowing quick will control the "high". On the other hand, when the vehicle speed SV is not equal to or higher than the vehicle speed b, the harvesting quick “low” control is performed in which the driving speed of the mowing unit 7 is driven at a constant speed at a low speed side of the vehicle speed synchronizing speed or a lower speed. When the vehicle is not moving forward, the harvesting quick “low” control for driving the mowing unit 7 at a constant speed at a low speed side of the vehicle speed tuning speed or at a low speed thereof or less is performed.

[0138] Furthermore, when the pouring switch 278, which is a quick-release pedal, is not operated and the pouring switch 278 is off, and the cutting speed is high, the driving speed of the mowing unit 7 is reduced. When the cutting speed is low, the vehicle speed tuning control is performed, and when the cutting speed is low, the driving speed of the cutting unit 7 is controlled at the cutting speed “low”.

[0139] As described above, the vehicle speed sensors 285 and 286 for detecting the vehicle speed and the driving speed of the reaping unit 7 are set to one of a low constant speed, a vehicle speed tuning speed, and a high constant speed. Since it is provided with the pouring pedal 277 which is a switching means for switching, it is possible to prevent the ears of the cereal culm from being handled and threshing in the raising operation of the cereal culm of the cutting section in the low-speed running and harvesting operation. On the other hand, an overload can be prevented in the high-speed traveling harvesting operation. Therefore, the harvester 7 can be properly driven at the low-speed constant speed or the high-speed constant speed in any of the low-speed traveling harvesting operation and the high-speed traveling harvesting operation, and the harvesting workability of the low-speed traveling harvesting operation is improved. In addition, the working efficiency of the high-speed running harvesting work can be improved.

[0140] Further, the low speed constant speed is higher than the vehicle speed S in the vehicle speed tuning section and the driving speed of the reaper 7 corresponding to a lower shift point at which the driving speed of the reaper 7 is switched to the lower constant speed. The driving speed of the mowing unit 7 is lower than the constant low speed when the mowing unit 7 is driven at the vehicle speed tuning speed along the vehicle speed tuning pattern. Thus, even if the vehicle speed in the vehicle speed tuning section is temporarily reduced to near the lower shift point, the driving speed of the reaper 7 is maintained at the vehicle speed tuning speed according to the vehicle speed tuning pattern, and It is possible to prevent the reaping unit 7 from being handled and raising the seeds and causing threshing.

[0141] Further, the high-speed constant speed is higher than the driving speed of the reaping unit 7 corresponding to a case where the vehicle speed in the vehicle speed tuning section is an upper shift point at which the driving speed of the reaping unit 7 is switched to the high-speed constant speed. The driving speed of the mowing unit 7 can be switched from the vehicle speed tuning speed according to the vehicle speed tuning pattern to the high-speed constant speed with a margin for the output of the engine 21 because it is set high. . The cutting section 7 is set to the vehicle speed tuning pattern. When the vehicle is driven at the vehicle speed synchronized speed along the speed, it is possible to smoothly shift to the high-speed traveling harvesting operation in which the cutting unit 7 is driven at the high-speed constant speed, and the work efficiency in the high-speed traveling harvesting operation can be improved.

[0142] Further, the switching means 277 controls the driving speed of the mowing unit 7 to be switched from a vehicle speed tuning speed to a constant low speed when the switching means 277 is switched when moving backward. It is. When the vehicle is traveling in reverse, the mowing unit 7 is in a stopped state. Therefore, even if the mowing unit 7 is driven from a stopped state, the driving of the mowing unit 7 is started at a low speed and a constant speed. The impact load at the time of starting the driving of the reaper 7 can be suppressed.

[0143] Further, while driving the reaping unit 7 at a vehicle speed tuning drive for changing the harvesting speed in synchronization with the vehicle speed or at a constant speed for driving the harvesting speed to be substantially constant, the constant speed pouring drive is performed. The speed is switched between high speed and low speed in two stages, and the mowing unit 7 is driven at the above-mentioned constant or high speed pouring drive speed. At any time of the work, the reaping unit 7 can be properly driven at the low-speed constant speed or the high-speed constant speed, thereby improving the harvesting workability of the low-speed traveling harvesting operation and improving the work efficiency of the high-speed traveling harvesting operation. Can be improved.

[0144] Further, the vehicle speed tuning speed of the reaping unit 7 for switching from the vehicle speed tuning drive to the high speed side constant speed pouring drive speed is configured to be lower than the low speed side constant speed pouring drive speed. Thus, in the entire range of the vehicle speed tuning speed of the mowing unit 7, the driving speed of the mowing unit 7 is increased by the switching operation of the operator, so that the operator can perform the driving operation without a sense of incongruity.

[0145] With reference to the flowchart in Fig. 32, harvesting operation control will be described. When the threshing switch 272 is turned on by operating the work lever 271, the feed chain solenoid 291 is turned off, the feed chain clutch 131 is turned on, the drive of the feed chain 5 is started, and the threshing clutch solenoid 297 is operated. The threshing clutch 97 is turned on to drive the threshing unit 4 and the feed chain 5.

When the cutting switch 273 is turned on by operating the work lever 271, the main transmission driving force is transmitted to the cutting unit 7 via the vehicle speed tuning pulley 93. At this time, the pouring pedal 277 When the pouring switch 278 is turned on by the stepping operation of the mowing unit 278, the cutting speed change slider 155 is set to the neutral position when the input speed of the vehicle speed tuning of the mowing unit 7 detected by the mowing input sensor 288 is equal to or less than the rotation setting by the pouring gear 123. Position, the harvesting speed change output of the harvesting speed change mechanism 151 is set to neutral, the transmission of the vehicle speed tuning input shaft 112 is turned off, and the pouring solenoid 292 is operated to move the mowing unit 7 through the pouring gear 123 at a high speed. It is driven at a lower speed than the cut gear 156.

[0147] On the other hand, when the pouring switch 278 is turned on and the input speed of the vehicle speed tuning of the mowing unit 7 is equal to or greater than the rotation set by the pouring gear 123, the mowing speed change output of the mowing transmission mechanism 151 is set to neutral and the tuning is performed. With the transmission of the input shaft 112 turned off and the operation of the high-speed cut solenoid 293, the mowing unit 7 is driven at a constant speed at a maximum rotation higher than that of the pouring gear 123 via the high-speed cut gear 156.

[0148] Further, when the auto-lift switch 280 is turned on when the pouring switch 278 is off, the mowing speed change output of the mowing speed change mechanism 151 is made neutral, and when the ground height of the mowing portion 7 is below the setting, The lifting cylinder 11 is operated to automatically raise the mowing part 7 to the set height, and the feed chain clutch 131 is disengaged. On the other hand, when the ground height of the mowing section 7 is higher than the setting, the mowing section 7 is automatically lowered to the mowing work height by the control of the lifting / lowering cylinder 11, and the feed chain clutch 131 is turned on. .

When the reverse switch 276 is turned on when the auto lift 280 is off, the cutting shift output of the cutting transmission mechanism 151 is neutralized, the solenoids 292 and 293 are turned off, and the switching slider 124 is turned off. Will be neutral.

[0150] When the reverse switch 276 is off and the axle 55 detected by the vehicle speed sensors 285 and 286 is stopped, the cutting speed change mechanism 151 is set to neutral and the vehicle speed synchronization drive of the cutting unit 7 is stopped. Will be. On the other hand, when the axle 55 is driven, when the sub-shift output of the speed change motor 39 is low, the input rotation of the reaping unit 7 detected by the reaping input sensor 288 for tuning the vehicle speed exceeds the rotation setting by the high-speed cut gear 156. At this time, the high speed cut solenoid 293 is operated, the cutting speed change mechanism 151 is neutralized, and a high speed cutting operation for driving the cutting unit 7 at a constant speed at the highest speed via the high speed cutting gear 156 is performed.

[0151] Further, the sub-shift output of the speed change motor 39 is low, and the input rotation of the reaper 7 is less than the setting. When the high-speed operation switch 275 is turned on when the automatic switch 284 is turned on and the automatic switch 284 is turned on, the input rotation of the mowing unit 7 is equal to or higher than the setting, and the mowing unit is connected to the mowing unit via the high-speed cut gear 156 in the same manner as described above. 7 is rotated at the highest speed at a constant speed to perform a high-speed cutting operation. In addition, by operating the high-speed operation solenoid 295 to engage the bypass clutch, the driving force of the engine 21 without passing through the traveling transmission member 40 is directly transmitted from the bypass clutch to the sub-transmission mechanism 47 to perform the high-speed operation operation. Become.

[0152] When the high-speed operation switch 275 is turned off, the cutting speed change output of the IJ cutting speed change mechanism 151 is switched to low speed or high speed by operating the cutting speed change switch 274. The reaper 7 is driven at a low speed or a high speed by a vehicle speed tuning input via one of the gears 152 and 153. The stalks that stand up can be harvested at low speed, or the stalks that lie down can be harvested at high speed.

As shown in FIG. 24, the cutting operation of the pouring pedal 277 during the mowing operation synchronized with the normal vehicle speed allows the mowing unit 7 to be moved at a low speed or a high speed via the pouring gear 123 or the high-speed cut gear 156. In the case of driving at a constant speed, the work speed when switching to the high-speed cut in which the driving is performed at a high speed is made different from the work speed when canceling the switching. Due to the output of the low-speed gear 152 (or high-speed gear 153) of the mowing transmission mechanism 151, the working speed (the number of rotations of the tuning input shaft 112) is changed to the vehicle speed a (or the vehicle speed b) in a cutting speed change (high or low speed) state. When the speed is increased as described above, the drive of the mowing unit 7 is switched to high-speed cutting (high-speed constant-speed driving).

[0154] Further, when the mowing quick operation is canceled, the working speed is reduced until the working speed at the high speed cutting release value reaches the vehicle speed c (or the vehicle speed d) by a fixed value smaller than the high speed cutting of the mowing drive speed. Maintain a fast cut. When the working speed becomes the vehicle speed c (or the vehicle speed d), the drive of the mowing unit 7 is returned to the normal speed change.

Claims

The scope of the claims

[1] The drive speed in the reaping unit is synchronized with the vehicle speed, and the vehicle speed is adjusted in accordance with the vehicle speed synchronization pattern that increases in proportion to the increase in the vehicle speed, or a substantially constant rotational speed set in advance regardless of the increase or decrease in the vehicle speed. In the combine which is configured to drive the mowing unit by switching to any one of

A vehicle speed sensor for detecting a vehicle speed;

Switching means for switching the speed of the mowing part in the drive vehicle speed tuning section to a constant low speed, a constant vehicle speed, or a constant high speed, or a shift.

[2] The constant low speed is lower than the drive speed of the reaper corresponding to when the vehicle speed in the vehicle speed tuning section is a lower shift point for switching the drive speed of the reaper to a lower constant speed. The combine according to claim 1, wherein the combine is set to a high value.

[3] The high-speed constant speed is higher than the drive speed of the reaper corresponding to when the vehicle speed in the vehicle speed tuning section is a higher-order transposition point for switching the drive speed of the reaper to the high-speed constant speed. 3. The combine according to claim 1, wherein the combine is set to be high.

[4] The switching means controls the driving speed of the reaping unit to be switched from a vehicle speed tuning speed to a low speed constant speed when the switching device is operated to switch backward. Item 3. The combine according to items 1 to 3.

[5] The reaping unit is driven by a vehicle speed tuning drive that changes the harvesting speed in synchronization with the vehicle speed or a constant speed pouring drive speed that keeps the harvesting speed substantially constant, while the constant speed pouring drive speed is increased. 2. The combine according to claim 1, wherein the harvester is driven at a constant high-speed or low-speed pouring drive speed by switching between two stages, i.e., low speed and low speed.

[6] The vehicle speed tuning speed of the reaper, which switches from the vehicle speed tuning drive to a high-speed constant speed pouring drive speed, is configured to be lower than the low speed constant speed pouring drive speed. A combine according to claim 4.