JPWO2005058010A1 - Combine - Google Patents

Abstract

When performing low-speed traveling harvesting work, while preventing the grain tip from being handled and shed by the grain-triggering work of the cutting part, this work efficiency is improved when performing high-speed traveling harvesting work. Provide a combine that prevents the drop. The driving speed in the cutting part is either the vehicle speed synchronization speed that follows the vehicle speed synchronization pattern that synchronizes with the vehicle speed and increases in proportion to the increase in the vehicle speed, or a substantially constant rotational speed that is set in advance regardless of the increase or decrease of the vehicle speed. In a combine configured to switch and drive the cutting unit, a vehicle speed sensor for detecting the vehicle speed, a cutting input sensor for detecting the rotational speed of the input shaft for driving the cutting unit, and driving of the cutting unit And a switching means for switching the speed to either a low constant speed, a vehicle speed synchronization speed, or a high constant speed.

Description

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

  Conventionally, a mission case for driving the traveling crawler, a mowing unit, and a threshing unit are provided. The driving force from the engine is transmitted to the threshing unit, the mowing unit, and the mission case, respectively. There is a technique in which the harvesting part is driven by either the vehicle speed synchronization speed output from the mission case or the substantially constant speed output from the engine to perform harvesting work (see, for example, Patent Document 1).

Conventionally, for example, when turning (changing direction) on a field headland, the driving speed of the cutting part is switched from a vehicle speed synchronization speed to a constant low speed, and the cereal of the cutting part is carried out to the threshing part, Clogging or the like in the harvesting portion was prevented (for example, see Patent Document 2).
Japanese Patent Laid-Open No. 10-286018 Japanese Patent Laid-Open No. 10-127146

  When harvesting cereals at the constant low speed, when the cereal conveyance speed in the reaper increases with respect to the vehicle speed (the speed of the combine), the tip of the cereal causes the cereal of the reaper. There was a problem that it was handled in the work and shattered.

  On the other hand, when the harvesting operation is performed at high speed, the driving load of the traveling crawler and the cutting unit that transmits the driving force from the transmission case increases, so the harvesting operation when the driving load is overloaded and the traveling is performed at high speed. There was a problem such as a decrease in efficiency.

  In view of such conventional problems, the present invention prevents the tip of the culm from being handled in the culm pulling work of the cutting part and shed. On the other hand, an object of the present invention is to provide a combine that prevents a reduction in work efficiency when performing a high-speed traveling harvesting work.

  In order to achieve the above object, the invention according to claim 1 is directed to increase or decrease the vehicle speed in accordance with a vehicle speed synchronization pattern that synchronizes the driving speed in the cutting unit with the vehicle speed and increases in proportion to the increase in the vehicle speed. Regardless of the combination configured to drive the cutting unit by switching to one of the preset substantially constant rotation speeds, the vehicle speed sensor for detecting the vehicle speed and the driving speed of the cutting unit are kept constant at a low speed. And switching means for switching to one of speed, vehicle speed synchronization speed, and high speed constant speed.

  According to a second aspect of the present invention, the low speed constant speed is based on the driving speed of the cutting part corresponding to when the vehicle speed in the vehicle speed tuning section is a lower shift point for switching the driving speed of the cutting part to the low speed constant speed. Is also set high.

  According to a third aspect of the present invention, the high speed constant speed is based on the driving speed of the cutting part corresponding to the vehicle speed in the vehicle speed tuning section when the vehicle speed is an upper shift point for switching the driving speed of the cutting part to the high speed constant speed. Is also set high.

  According to a fourth aspect of the present invention, the switching means controls the driving speed of the reaping portion to be switched from a vehicle speed synchronized speed to a low constant speed when the switching means is switched during reverse travel. It is.

  According to a fifth aspect of the present invention, the cutting unit is driven at a vehicle speed-synchronized drive that changes the cutting speed in synchronization with the vehicle speed or a constant driving speed that keeps the cutting speed substantially constant, while the constant speed driving is driven. The speed is switched between two stages, high speed and low speed, and the mowing unit is driven at the constant speed casting driving speed of high speed or low speed.

  The invention according to claim 6 is configured such that the vehicle speed synchronization speed of the cutting part for switching from the vehicle speed synchronization drive to the constant speed driving driving speed on the high speed side is lower than the constant speed driving driving speed on the low speed side. It is.

  Since the invention which concerns on Claim 1 is provided with the switching means which switches the driving speed of the said cutting part to either a low speed constant speed, a vehicle speed synchronous speed, or a high speed constant speed, It is possible to prevent the grain tips from being handled and shattered during the raising operation of the harvesting unit. On the other hand, it is possible to prevent an overload in a high-speed traveling harvesting operation. Therefore, at any time of the low-speed traveling harvesting work or the high-speed traveling harvesting work, the harvesting unit can be appropriately driven at the low-speed constant speed or the high-speed constant speed, and the harvesting workability of the low-speed traveling harvesting work is improved. In addition, the work efficiency of high-speed traveling harvesting work can be improved.

  According to a second aspect of the present invention, the low speed constant speed is based on the driving speed of the cutting part corresponding to when the vehicle speed in the vehicle speed tuning section is a lower shift point for switching the driving speed of the cutting part to the low speed constant speed. Also, since it is set high, when driving the cutting part at a vehicle speed synchronization speed that follows the vehicle speed synchronization pattern, so that the driving speed of the cutting part is lower than the low speed constant speed, Even if the vehicle speed in the vehicle speed tuning section is temporarily decelerated to near the lower shift point, the driving speed of the cutting part is maintained at the vehicle speed synchronizing speed according to the vehicle speed tuning pattern, and the tip of the cereal is raised by the cutting part. It can be prevented from being shattered by handling.

  According to a third aspect of the present invention, the high speed constant speed is based on the driving speed of the cutting part corresponding to the vehicle speed in the vehicle speed tuning section when the vehicle speed is an upper shift point for switching the driving speed of the cutting part to the high speed constant speed. However, since the engine output is set high, it is possible to switch the driving speed of the cutting unit from the vehicle speed tuning speed according to the vehicle speed tuning pattern to the high speed constant speed. When the cutting unit is driven at a vehicle speed synchronization speed that follows the vehicle speed synchronization pattern, the cutting unit can smoothly shift to the high-speed traveling harvesting operation that drives at the high-speed constant speed. Can be improved.

  According to a fourth aspect of the present invention, the switching means controls the driving speed of the reaping portion to be switched from a vehicle speed synchronized speed to a low constant speed when the switching means is switched during reverse travel. It is. Since the mowing unit is in a stopped state during reverse travel, even when the mowing unit is driven from a stopped state, the mowing unit starts driving at a low constant speed, so that the mowing unit The impact load at the start of driving can be suppressed.

  According to a fifth aspect of the present invention, the cutting unit is driven at a vehicle speed-synchronized drive that changes the cutting speed in synchronization with the vehicle speed or a constant driving speed that keeps the cutting speed substantially constant, while the constant speed driving is driven. Since the speed is switched between high speed and low speed in two stages, and the cutting unit is driven at the constant or high speed casting driving speed, the low speed traveling harvesting work or the high speed traveling harvesting work is performed. In any case, the harvesting unit can be appropriately driven at the low speed constant speed or the constant high speed, so that the harvesting workability of the low speed traveling harvesting work can be improved and the work efficiency of the high speed traveling harvesting work can be improved.

  The invention according to claim 6 is configured such that the vehicle speed synchronization speed of the cutting part for switching from the vehicle speed synchronization drive to the constant speed driving driving speed on the high speed side is lower than the constant speed driving driving speed on the low speed side. Therefore, the driving speed of the cutting unit is increased by the operator's switching operation over the entire range of the vehicle speed synchronization speed of the cutting unit, and the operator can operate the vehicle without a sense of incongruity.

FIG. 1 is a left side view of a 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 the front aircraft.
FIG. 5 is an explanatory plan view of the machine base.
FIG. 6 is an enlarged view of a counter case part.
FIG. 7 is a side view of the front airframe.
FIG. 8 is an enlarged view of the same part.
FIG. 9 is a side view of the counter case part.
FIG. 10 is an output system diagram of the engine.
FIG. 11 is a drive system diagram of a mission case.
FIG. 12 is a hydraulic circuit diagram.
FIG. 13 is a cross-sectional view of a counter case.
FIG. 14 is a diagram of the same drive system.
FIG. 15 is a modified explanatory view of FIG.
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 explanatory 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 part.
FIG. 21 is a control circuit diagram.
FIG. 22 is a flowchart of the cutting part speed control.
[FIG. 23] A diagram showing the relationship between the cutting rotational speed KVx of the cutting drive shaft for driving the cutting unit and the vehicle speed SV.
FIG. 24 is a diagram showing the relationship between the cutting speed KVx of the cutting transmission shaft and the vehicle speed SV when the shifting of the cutting unit is high and low.
FIG. 25 is a control circuit diagram.
FIG. 26 is an explanatory diagram of a display screen of the liquid crystal panel.
FIG. 27 is an explanatory diagram of a display screen of the 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 the harvesting quick control.
FIG. 31 is an output diagram of harvesting quick control.
FIG. 32 is a flowchart of harvesting operation control.

Explanation of symbols

7 Cutting part 112 Input shaft 277 Pour pedal (switching means)
285, 286 Vehicle speed sensor 288 Cutting input sensor

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

  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 installed, a machine base installed between the left and right track frames 1, and a feed chain 5 stretched on the left side. In addition, the threshing unit 4 including the handling cylinder 6 and the processing cylinder 6a, the reaping mechanism 8, the cutting blade 9, and the reaping conveyance mechanism 10 are arranged, and the reaping unit 7 is connected to the reaping frame 12 so as to move up and down. A hydraulic lifting cylinder 11 that performs, a waste disposal unit 13 that faces the end of the waste chain 14, a grain tank 15 that carries the grain from the threshing unit 4 through the milled cylinder 15 a, A vertical and horizontal discharge augers 16 and 17 for carrying grains out of the machine, a driving cabin 18 in which a driving operation handle 19 and a driving seat 20 are installed, and an engine 21 installed below the driving cabin 18 are provided. Harvests culms continuously are configured to threshing.

  With reference to FIG. 4 thru | or FIG. 10, the structure of the body of the combine of this invention is demonstrated. A mission case 22 is disposed between the left and right traveling crawlers 2 on the front side of the machine base 3. The transmission case 22 and the engine 21 are installed substantially in series, and the driving force from the engine 21 is transmitted to the traveling crawler 2 via the transmission case 22.

  Left and right support bases 23 and 24 are erected on the upper surface of the machine base 3 on the front side of the threshing unit 4. On the left and right support bases 23 and 24, the cutting unit 7 is installed through the cutting frame 12 so as to be movable up and down and laterally movable. A counter case 25 is installed on the upper surface of the machine base 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 cutting unit 7 via the counter case 25. (See FIG. 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 mission 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 the upper part of the cabin front frame 26 via the rotation fulcrum shaft 28.

  A left cabin rear frame 29 is erected on the right support base 24. The engine 21 is installed on the upper surface of the machine base 3, and the engine 21 is arranged between the right cabin rear frame 30 and the left cabin rear frame 29 erected on the machine base 3. An engine room cover 31 covering the engine 21 is installed (see FIG. 4).

  Further, the upper parts of the left and right rear cabin frames 29 and 30 are connected by a cabin lateral frame 32, and the cabin lateral frame 32 is disposed above the engine room cover 31. The rear portion of the step frame 27 and the cabin horizontal frame 32 are detachably connected via the base bracket 33 (see FIG. 4).

  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, 35 are configured to ensure the rigidity of the cabin front frame 26 (see FIG. 5). .

  Further, the auger support 36 is connected to the left cabin rear frame 29, and an auger rest 37 for supporting the discharge auger 17 that can be moved up and down and swiveled in the storage position is installed on the upper side of the auger support 36. (See FIG. 7).

  Further, a configuration for transmitting the driving force of the engine 21 to the mission case 22 will be described with reference to FIGS. 10 to 12. The transmission case 22 includes a traveling transmission member 40 that forms a hydraulic continuously variable transmission mechanism for traveling main transmission, which includes 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 that forms a hydraulic continuously variable transmission mechanism 42 for turning. The input shaft 45 of the mission case 22 is connected to the output shaft 44 of the engine 21. The traveling pump 38 and the swing pump 41 are configured to be driven by the output from the engine 21.

  The differential mechanism 48 has a pair of symmetrical planetary gear mechanisms 50. Each planetary gear mechanism 50 includes one sun gear 51, three planetary gears 52 that mesh with the outer periphery of the sun gear 51, and a ring gear 53 that meshes with these planetary gears 52 (see FIG. 11).

  Left and right carriers 56 for rotatably supporting the planetary gear 52 are installed on the left and right axles 55 on the same axis as the free-wheeling 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 driving wheels 49 are pivotally supported on the axle 55, and the driving 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 FIG. 11).

  The traveling speed change member 40 is configured to control the forward / reverse rotation and the rotational speed of the traveling motor 39 by changing the swash plate angle of the traveling pump 38. The rotation of the travel 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 carriers 56 are transmitted. Is configured to rotate (see FIG. 11). The parking brake 61 is disposed on the brake shaft 59.

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

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

  The steering output brake 63 is disposed on the motor shaft 64, the steering output clutch 65 is disposed on the clutch shaft 66, and the left and right input gears 67 and 68 are always meshed 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 output of the turning motor 42 and the steering output clutch 65. The left and right input gears 67 and 68 are connected to the clutch shaft 66 through the forward rotation gear 69 and the reverse rotation gear 70 (see FIG. 11).

  When the rotational force of the motor 42 is transmitted to the right sun gear 51 via the forward rotation gear 69, while the rotational force of the motor 42 is transmitted to the left sun gear 51 via the reverse rotation gear 70, and the turning motor 42 is rotated forward (reverse). The left sun gear 51 is reversely rotated (forward) at the same left and right rotational speed, while the right sun gear 51 is rotated forward (reversely) so that the left and right traveling crawlers 2 are driven in the reverse direction at the same speed. . Further, the turning member 43 forming the turning hydraulic continuously variable transmission mechanism is configured to perform forward / reverse rotation and rotation speed control of the turning motor 42 by changing the swash plate angle of the turning pump 41. (See FIG. 11).

  Therefore, when the turning motor 42 is stopped and the left and right sun gears 51 are stopped, the rotation of the traveling motor 39 is transmitted to the left and right ring gears 53 at the same rotational speed when the traveling motor 39 is driven. For this reason, the left and right traveling crawlers 2 are transmitted with the driving force of the same rotational speed in the left and right directions and the same number of rotations via the carrier 56, so that the airframe moves straight forward in the front-rear direction by driving the left and right traveling crawlers 2. (See FIG. 11).

  On the other hand, when the traveling motor 39 is stopped and the left and right ring gears 53 are stopped, when the turning motor 42 is driven in the forward rotation (or reverse rotation) direction, the left planetary gear mechanism 50 rotates forward (or reverse rotation). On the other hand, the planetary gear mechanism 50 on the right side reverses (or rotates forward) and drives the left and right traveling crawlers 2 in opposite directions, so that the body turns in the left or right direction by driving the left and right traveling crawlers 2. (See FIG. 11).

  On the other hand, when both the traveling motor 39 and the turning motor 42 are driven at the same time, the aircraft moves in the front-rear direction and turns in the left-right direction, so that the course of the aircraft can be corrected. The turning radius of the airframe is determined by the output rotation speed of the turning motor 42.

  As shown in FIGS. 10 and 11, a cooling fan 72 of a radiator for water cooling of the engine 21 is provided, the cooling fan 72 is disposed 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 and 74 of the traveling and turning pumps 38 and 41 through a gear group 75. The input shaft 45 is connected to the pumps 38 and 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 vehicle speed constant speed clutch 76. The pump shaft 73 and the motor shaft 46 are gear-connected through the constant speed shaft 77 when the vehicle speed constant speed clutch 76 is engaged.

  The rotation of the input shaft 45 is transmitted to the auxiliary 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 and harvest. It is configured to perform work or the like (see FIG. 11). The charge pump 78 is connected to the swing pump shaft 74.

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

  When the speed change valve 82 is switched by the main speed change lever 81, the main speed change cylinder 80 is actuated to change the angle of the swash plate 79 of the travel pump 38, thereby changing the rotational speed of the motor shaft 46 of the travel motor 39 steplessly. Or a reverse shift operation is performed, while a feedback operation is performed so that the shift valve 82 is neutrally returned by the angle adjustment operation of the swash plate 79, and the angle of the swash plate 79 depends on the amount of operation of the main transmission lever 81. The vehicle speed is changed by changing the rotational speed of the travel motor 39 (see FIG. 12).

  Further, 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 connected to the charge pump 78 and the electromagnetic sub transmission valve 86. It is formed so as to be hydraulically connected through. When the sub-transmission valve 86 is neutral, the sub-transmission cylinder 85 is short-circuited to the transmission case 22 which is an oil tank, and the swash plate 84 angle of the travel motor 39 is changed by the main circuit hydraulic pressure, while the swash plate 84 angle is sub- The output of the traveling motor 39 is changed to a high speed or a low speed by forcibly changing the speed change valve 86.

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

  When the turning valve 89 is switched by the steering handle 19, the turning cylinder 88 is activated to change the angle of the swash plate 87 of the turning pump 41, thereby changing the rotation speed of the motor shaft 64 of the turning motor 42 steplessly. The angle of the swash plate 87 is changed to the operation of the steering handle 19 by performing a feedback operation so that the turning valve 89 is neutrally returned by the angle adjusting operation of the swash plate 87 while performing the left and right turning operation to be reversed. It changes in proportion to the amount, and the rotational speed of the turning motor 42 is changed to change the left and right turning angle (see FIG. 12).

  Further, when the main transmission lever 81 is operated to a position other than the neutral position and the steering handle 19 is operated to other than straight travel, the hydraulic output of the traveling pump 38 is proportional to the operation direction and the operation amount of the main transmission lever 81. When the hydraulic motor 39 is rotated forward / reversely or increased / decreased to change the forward / reverse speed (vehicle speed), the output of the swing pump 41 changes in proportion to the operation amount of the main transmission lever 81 (FIG. 12). reference).

  When the main shift lever 81 is operated, the turning radius is automatically reduced by the high-speed traveling shift, and the turning radius is automatically increased by the low-speed traveling shift, while the steering handle 19 is operated. In addition, the turning radius of the left and right traveling crawler 2 is maintained substantially constant regardless of the traveling speed, and the working traveling speed is changed and the course is corrected so that the machine body is aligned with the uncut grain culvert.

  On the other hand, when the valves 82 and 89 are controlled, the output of the swing 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) is reduced ( If it is increased), the traveling speed (vehicle speed) is reduced in proportion, and the speed difference between the left and right traveling crawlers 2 is increased, and the vehicle turns left and right.

  Accordingly, the driving speed of the left and right traveling crawler 2 is changed to correct the alignment course and change the direction by spin turn at the field headland, and the harvesting operation of continuously harvesting and threshing the cereal is performed. When the main transmission lever 81 is neutral, the swing valve 89 is maintained neutral regardless of the operation of the steering handle 19, so that the hydraulic output of the swing pump 41 is maintained at substantially zero and the swing motor 42 is stopped. Configure.

  Next, the transmission structure of the counter case 25 will be described with reference to FIGS. The output shaft 44 of the engine 21 protrudes from the front side and the rear side of the counter case 25. The front side of the output shaft 44 is connected to the input shaft 45. A work output pulley 91 is disposed on the rear side of the output shaft 44. A counter case 25 is installed on the machine base 3 in front of the threshing unit 4 on the left side of the engine 21. 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. The input pulley 92 on the rear side of the counter case 25 is connected to the work output pulley 91 via a tension threshing clutch 97 so that the driving force from the engine 21 is transmitted to the counter case 25 via the input pulley 92. Constitute.

  The vehicle speed tuning pulley 93 on the right side of the counter case 25 is connected to the cutting drive pulley 62 of the transmission case 22 via the idle pulley 99 on the front side of the right support 24. A mowing input pulley 103 is pivotally supported on the left side of the case 101 via the mowing input shaft 102, and a mowing pulley 95 on the left side of the counter case 25 is connected to the mowing input pulley 103 with a belt 104. The driving force is transmitted (see FIG. 10). The cutting input case 101 is rotatably supported on the support bases 23 and 24, the cutting frame 12 is connected to the case 101, and the cutting unit 7 is rotated around the case 101 to be moved up and down.

  Next, the threshing pulley 94 on the front side of the counter case 25 is connected to the driving input pulley 105 of the handling cylinder 6 by a belt 106, and the driving force from the sorting pulley 96 is applied to the sorting trap and the swinging sorting mechanism below the handling cylinder 6. And configured to drive each part of the threshing unit 6. On the other hand, the feed chain input shaft 107 is provided on the left side surface of the counter case 25, and the drive sprocket 108 of the feed chain 5 is movably disposed on the feed chain input shaft 107 to drive the power from the input shaft 107. It is configured to transmit to the 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 belt-connected to the work output pulley 91 via a discharge clutch 110, and the output from the engine 21 is transmitted to the discharge auger 17 so that the grains in the tank 15 are discharged (see FIG. 10). ).

  As shown in FIG. 14, the barrel input shaft 111 is pivotally supported on the counter case 25, and the shaft 111 extends in the front-rear direction of the counter case 25. The threshing pulley 94 is installed at the front end portion of the shaft 111 that protrudes outside the front surface of the counter case 25, while the input pulley 92 is installed at the rear end portion of the shaft 111 that protrudes outside the rear surface of the counter case 25, A constant rotational power from the engine 21 is input to the cylinder input shaft 111, and the input shaft 111 is configured to rotate 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 outer side of the counter case 25, and the vehicle speed tuning pulley 93 is disposed on the right end of the shaft 112, 100 is tensioned between the pulleys 62 and 93 via the idle pulley 99, and the vehicle speed synchronization power is input from the mission case 22 to the counter case 25 (see FIG. 10).

  Further, a counter speed shaft 114 that is a counter shaft or a selection input shaft connected to the handle cylinder input shaft 111 via a bevel gear 113, and a vehicle speed tuning shaft 115 that is arranged substantially in parallel with the front side of the shaft 114 are provided in a counter case. 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 the power from the vehicle speed tuning pulley 93 is transmitted by the one-way clutch 120. When transmitted to the gear 117, the vehicle speed tuning shaft 115 is configured to rotate via the gear 117 and the cutting clutch 118 (see FIG. 14).

  Further, a cutting constant speed clutch 122 for forming the cutting constant speed mechanism 121 and a high speed cut gear 123 are installed on the shafts 114 and 115, and the shafts 114 and 115 are connected via the clutch 122 and the gear 123. When one of the gear clutches 118 and 122 is selectively engaged by the switching slider 124, the cutting unit 7 is driven at a driving speed synchronized with the vehicle speed, while the cutting unit 7 is driven at the vehicle speed synchronization speed. It is driven at a faster high speed constant speed (high speed cutting drive speed) to cut the fallen cereal meal (see FIG. 14).

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

  Accordingly, the vehicle speed tuning input and the constant speed drive input transmitted to the torque limiter 126 are simultaneously turned on / off and the constant speed drive input on / off by the same slider 124. Therefore, the vehicle speed tuning input and the constant speed drive input are selected and transmitted by the slider 124, and transmission switching control becomes unnecessary, thereby improving handling.

  On the other hand, the case of the gear 128 is installed on the left support base 23 so as to be rotatable about the vertical axis via the fulcrum shaft 199, the left side of the cutting input case 101 is fixed to the case of the gear 128, and the gear 128 is fixed to each case 101. The cutting transmission shaft 130 can be inserted into the cutting frame 12 on the right end side of the case 101, the cutting power is input from the left end side of the cutting input shaft 102, and the driving of the cutting unit 7 is driven by the cutting transmission shaft. On the other hand, the cutting part 7 can be rotated and moved substantially horizontally around the fulcrum shaft 129 to the left side of the machine body to perform maintenance and the like in the vicinity of the cases 22 and 25 inside the machine body.

  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 chain 133 through a feed chain clutch 131 to a feed chain drive shaft 132, so that the rotation of the constant speed shaft 114 is transmitted by changing the rotation speed of the vehicle speed tuning shaft 115. A chain transmission mechanism 134 is installed.

  The feed chain mechanism 134 is formed to be continuously variable by a planetary gear mechanism 138 including a sun gear 135, a planetary gear 136, and a ring gear 137. The sun gear 135 is pivotally supported on the constant speed shaft 114, the ring gear 137 is idled and supported on the constant speed shaft 114, and 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 loosely supported on the bearing body 140, the bearing body 140 is idlely supported on the constant speed shaft 114, and the bearing body 140 is connected to the feed chain drive shaft via the feed chain clutch 131 and the gear 141. By connecting to 132, the minimum rotation required for the conveyance of the cereal is ensured, and the speed of the feed chain 5 can be changed from the low constant rotation to the high rotation in synchronization with the vehicle speed (see FIG. 14). ).

  Also, a hydraulic cutting speed cylinder 143 for operating the switching slider 124 and a hydraulic threshing cylinder 144 for turning on the threshing clutch 97 are fixed to an oil passage base 145 that is a top cover of the counter case 25. . On the other hand, a vehicle speed constant speed cylinder 146 for turning on the vehicle speed constant speed clutch 76, 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 configured to be hydraulically connected in parallel to the charge pump 78 (see FIG. 12).

  Next, with reference to FIGS. 15 and 16, a configuration in which the cutting speed change mechanism 151 for switching the driving speed of the cutting unit 7 is installed in the counter case 25 will be described. Using the counter case 25 having the same shape as the counter case 25 of FIG. 13 with the specification not provided with the cutting speed change mechanism 151, the specification with the cutting speed change mechanism 151 is configured. The low speed gear 152 and the high speed gear 153 forming the cutting transmission mechanism 151 are disposed between the tuning input shaft 112 and the cutting transmission shaft 154. A cutting speed change slider 155 that performs low speed, neutral, and high speed cutting speed changes is provided, and when either of the gears 152 and 153 is selectively engaged with the cutting speed change shaft 154 via the cutting speed change slider 155, the cutting speed change speed change is performed. The cutting speed change output is transmitted to the vehicle speed tuning shaft 115 that connects the shaft 154 on the same axis.

  On the other hand, an inflow gear 123 and a high speed cut gear 156 that are provided with a high speed cut gear 156 and form the cutting and fixing speed mechanism 121 are installed between the shafts 114 and 115. There is provided a switching slider 124 for driving the cutting unit 7 at a low constant speed (flow driving speed) or a high constant speed (high cut driving speed), and the gears 123, 156 are connected to the shafts 114, 156 by the switching slider 124. When engaged alternatively with 115, the mowing unit 7 is driven at a constant low speed (inflow), and the grain of the mowing unit 7 is conveyed to the feed chain 5 side at a constant rotational speed regardless of the vehicle speed. become. On the other hand, the mowing unit 7 is driven at a constant high speed (high speed cut), and the mowing unit 7 is driven at a constant rotational speed faster than the vehicle speed synchronization speed to trim the fallen cereal meal (see FIG. 16).

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

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

  On the other hand, when 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 lid 158 can be put in and out of the mounting hole 157 with the gear 161 mounted on the shaft 125 ( (See FIG. 18). A flat gear 163 for meshing with the gear 161 is supported on the vehicle speed tuning shaft 115 as an engagement shaft, and the limiter transmission gear 161 is connected to the vehicle speed tuning shaft 115 (see FIG. 16).

  Next, the torque limiter 126 has the same circular shape as the cylindrical outer case 164 integrally formed on the side surface of the limiter transmission gear 161 and the donut plate-shaped receiving plate 165 and the 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 circumference at substantially equal intervals, and the torque roller 167 of the torque plate 168 are supported from opposite sides of the cutting transmission shaft 125 in the axial direction. A donut plate-shaped inner plate 169 and outer plate 170, and a detachable nut 171 and a washer 172 that are screwed onto the transmission shaft 125 and pressed against the push plate 166 are provided (see FIG. 19). Note that the outer case 164 on the main body side of the torque limiter 126 is disposed inside the counter case 25, and the outer case 164 and the like are configured to be oil bathed.

  As shown in FIGS. 18 and 19, the cutting transmission shaft 125 is pivotally supported on the bearing lid 158, the limiter transmission gear 161 is pivotably supported on the cutting transmission shaft 125, and the receiving plate 165 is disposed inside the outer case 164. The inner plate 169, the torque plate 168, and the outer plate 170 are inserted into the hole 173, and the inner case 164 is inserted into the outer case 164, and the inner hole of the inner plate 169 is engaged and supported by 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 intervals of approximately 120 degrees. Further, when the torque spring 176 is supported on the seat plate 177, the seat plate 177 is rotatably supported on the machine outer end portion of the cutting transmission shaft 125, and the torque nut 178 is screwed to the shaft 125, the torque limiter 126 is attached. The bearing lid 158 and the cutting transmission shaft 125 are assembled into a unit structure. The torque nut 178 is tightened to adjust the force of the torque spring 176, and the transmission torque of the torque roller 167 is set (see FIG. 18).

  On the other hand, the cutting pulley 95 and the pulley boss 179 are separately formed, the pulley 95 and the pulley boss 179 are detachably fastened by a bolt 180, the pulley boss 179 is key-fitted to the cutting transmission shaft 125, and the pulley boss 179 A torque nut 178 and a spring 176 are arranged outside the counter case 25 so that the torque spring 176 is pressed against the outer surface of the machine (see FIG. 18).

  An L-shaped oil hole 181 is formed in the shaft core portion of the cutting transmission shaft 125, one end side of the oil hole 181 is opened to the end surface of the shaft 125 in the counter case 25, and the other end side of the oil hole 181 is cut and transmitted. When the shaft 125 opens to the peripheral surface, the centrifugal force generated by the rotation of the cutting 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 moved by the centrifugal force. The torque roller 167 is forcibly sent and forcedly lubricated (see FIG. 17).

  On the other hand, a rectangular support hole 182 similar in plan view to the cylindrical shape of the torque roller 167 is formed in the torque plate 168. The torque roller 167 is rotatably inserted into the support hole 182. A pair of tongue pieces 183 are formed to face each other at the opening edge on the long side where the support hole 182 faces, 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).

  Further, the bending edge 184 is formed on the outer periphery of the torque plate 168, the tongue piece 183 is projected in the same direction as the bending edge 184, and the thickness of the torque plate 168 (the width in the axial direction) is set to the torque roller 167. If it is smaller than the outer diameter, the outer peripheral side of the torque roller 167 protrudes on both side surfaces of the torque plate 168, and the torque roller 167 is in 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 periphery of the torque roller 167 is rotatably held by the pair of tongue pieces 183 ( FIG. 20).

  Note that the torque roller 167 and the torque plate 168 are arranged such that the axis of the torque roller 167 is inclined at a certain inclination angle toward the lower rotation side of the torque plate 168 with respect to radiation passing through the rotation center of the torque plate 168. Install in. The torque roller 167 is disposed on the torque plate 168 so that the rolling axis of the torque roller 167 is inclined by a certain angle with respect to a plane (radiation) including the rotation center of the torque plate 168, and the vehicle speed tuning shaft 115. When the outer case 164 is rotationally driven via the spur 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 torque roller 167 tries to roll in a direction inclined by a certain angle with respect to the rotation track of the outer plate 170 in the direction of the rotation track of the outer plate 170 while being restricted by the torque plate 168. Therefore, a frictional resistance proportional to the torque spring 176 pressure is generated.

  Moreover, since each torque roller 167 generates sliding friction while rolling, no static friction is generated, and a stable frictional resistance force by dynamic friction is always obtained. On the other hand, when the cutting drive load on the cutting transmission shaft 125 side increases or when the rotational speed of the outer case 164 suddenly changes to the high speed side by changing the input speed on the flat gear 163 side, the inner plate 169 and the outer plate 170 , Each rotational torque difference 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 to interrupt the transmission power.

  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 cutting unit 7 as the working unit. The torque limiter 126 is disposed on the cutting transmission shaft 125 for rotating the cutting unit 7. Even if a shock occurs due to a difference in driving torque when the hydraulic transmission mechanism 40 and the constant speed mechanism 121 are switched, the shock can be absorbed by the torque limiter 126. On the other hand, by making the hydraulic oil surface in the counter case 25 for installing the torque limiter 126 higher than the installation position of the shaft 125 of the torque limiter 126, the hydraulic oil is sufficiently supplied to the torque limiter 126. Can be lubricated.

  On the other hand, when the torque nut 178 and the torque spring 176 are installed outside the pulley boss 179, the torque set of the torque limiter 126 can be performed from the outside of the machine, and the handling property such as maintenance can be improved. When the cutting pulley 95 and the pulley boss 179 are formed separately and the cutting pulley 95 and the pulley boss 179 are fastened with the bolt 180, the cutting pulley 95 can be removed with the pulley boss 179 attached, and the torque limiter 126 The belt pulley can be replaced by removing the cutting pulley 95 with the set torque kept constant.

  Further, as shown in FIGS. 19 and 20, the receiving plate 165 and the pressing plate 166 are opposed to each other on the rotating shaft 125. A plurality of sets of inner plate 169, torque plate 168, and outer plate 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 to the rotating shaft 125, the spring seat plate 177 is locked to the torque nut 178, and the spring 176 is disposed between the spring seat plate 177 and the push plate 166. The receiving plate 165 or the pressing plate 166 is formed so that the pressure receiving surfaces 185 and 186 face 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 bent by a pressing force that generates a set torque.

  Each of the pressure receiving surfaces 185 and 186 of the receiving plate 165 and the pressing plate 166 has a taper structure having the inclination angles A1 and A2. Each of the pressure receiving surfaces 185 and 186 is formed as a taper having inclination angles A1 and A2 so that the outer peripheral sides of the receiving plate 165 and the pressing plate 166 first contact the inner plate 169 (see FIG. 20).

  Accordingly, since the receiving plate 165 or the pressing plate 166 is bent 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 surface of the torque roller 167, and the torque Uneven wear of the roller 167 can be reduced, durability can be improved, and set torque transmission accuracy can be improved. Even if the receiving plate 165 or the pressing plate 166 is not thick enough to be distorted by the set torque, the surface pressure of the pressure receiving surfaces 185 and 186 can be smoothed, so a space-saving and compact unit is configured. It will be possible.

  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 formed in contact with the inner portion 188 of the bearing bearing 162 so as to receive the set torque. Further, when the step plate 166 is provided with a step portion 189 and the step portion 189 is brought into contact with the washer 172, the circumferential side of the press plate 166 is between the washer 172 fixed by the nut 171 and the press plate 166. As a result, the tightening force of the nut 171 acts linearly from the step 189 to the pressing plate 166 via the washer 172.

  As shown in FIG. 17, when a shaft cover 191 made of synthetic resin is fixed to the pulley boss 179 with screws 190 and a torque spring 176, a torque nut 178, etc. are installed in the shaft cover 191, the shaft cover 191 is removed. Thus, 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. Further, when oil holes 181 are opened at a plurality of locations on the outer periphery of the rotating shaft 125 corresponding to the gaps between the plurality of inner plates 169, the oil flows from the oil holes 181 to the key grooves of the outer case 164. The torque roller 167 can be forcibly lubricated by moving to the outside of the outer case 164 via the 174 by centrifugal force.

  As is apparent from the above, when the oil holes 181 are formed in a plurality of closed portions partitioned by the inner plate 169 so as to be oilable, the inner plate 169, the outer plate 170, and the torque plate 168 are formed in a multilayer shape. Even if it is provided, 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.

  Further, when the oil in the blocking portion is discharged from the key groove 174 of the outer case 164 with which the outer plate 170 is engaged, the oil around the torque roller 167 can be efficiently discharged from the key groove 174 by centrifugal force, and the torque roller 167 Therefore, the oil can be supplied more efficiently, and the torque roller 167 can be lubricated efficiently. On the other hand, when a space is formed between the washer 172 and the pressing plate 166 on the circumferential side of the pressing plate 166, the tightening force of the nut 171 is applied directly to the pressing plate 166 via the washer 172, and the pressing plate 166 is pressed. The pressure receiving surface 186 of the plate 166 is smoothed to prevent the uneven load of the torque roller 167.

  Further, as shown in FIGS. 1 to 4 and 9, a column controller 192 installed in the cabin 18 on the rear side of the driver's seat 20 and a travel controller 194 installed on the front plate 193 of the left and right support bases 23, 24. And an engine controller 195 installed on the cabin frame 30 outside the engine room cover 31 and a threshing controller 196 installed on the threshing unit 4 machine frame on the rear side of the grain tank 15. The controllers 192, 194, 195, and 196 are configured to be connected by CAN communication.

  On the other hand, a hydraulic valve set 197 for moving the cutting unit 7 up and down, leveling the machine body, 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). An outside air introduction cover 198 disposed outside the engine room cover 31 and a grain tank 15 that rotates horizontally around the vertical discharge auger 16 are provided. The grain tank 15 and the outside air introduction cover 198 are rotatably installed on the side of the machine body (see FIG. 3). A storage case 200 for installing a part of the gear 128 is installed on the upper portion of the left support base 23 so as to be rotatable around the vertical axis via a fulcrum shaft 199 (see FIG. 4). The storage case 200 is disposed on the left side of the cutting input case 101 for supporting the cutting frame 12. A part of the gear 128 is installed in the cutting input case 101 (see FIG. 10). The driving force of the cutting unit 7 is input from the left end side of the cutting input shaft 102 and is transmitted to the cutting transmission shaft 130 inserted in the cutting frame 12. On the other hand, when the cutting unit 7 is pivoted laterally about the fulcrum shaft 199 toward the left side of the machine body, maintenance and the like near the cases 22 and 25 inside the machine body can be performed.

  Further, as shown in FIGS. 13 and 15, the power from the engine 21 is transmitted to the mission case 22 for driving the traveling crawler 2, the mowing unit 7 and the threshing unit 4 through the counter case 25. In the combine, the specification of FIG. 15 provided with the cutting transmission mechanism 150 for changing the driving speed of the cutting unit 7 and the specification of FIG. 13 without the cutting transmission mechanism 150 are replaced with the counter case 25 having the same shape. When used, the counter case 25 can also be used for a plurality of different specifications, and the manufacturing cost can be reduced.

  Further, when the cutting unit 7 is driven by switching the driving speed of the cutting unit 7 from the vehicle speed synchronization speed to the constant driving speed (flowing speed), the cutting unit when the specifications of FIG. Compared with the constant drive speed of FIG. 7, the fixed drive speed (flowing speed) of the cutting unit 7 when the specification of FIG. It can be driven accordingly.

  Further, in the specification of FIG. 15 in which a cutting transmission mechanism 150 for changing the driving speed of the cutting unit 7 is provided, a pouring gear 123 that is a pouring mechanism and a high speed cutting gear 156 that is a high speed cutting mechanism are installed in the counter case 25. To do. On the other hand, in the specification of FIG. 13 in which the cutting speed change mechanism 150 is not provided, the specification of FIG. 15 in which the cutting speed change mechanism 150 is provided can be obtained by simply replacing the pouring gear 123 and the shaft 154 by removing the high speed cut gear 156. The specification shown in FIG. 13 without the speed change mechanism 150 can be configured, and the manufacturing cost can be reduced.

  On the other hand, since the installation position of the travel controller 194 is opened by the lateral rotation of the cutting unit 7, the travel controller 194 is located on the inner side of the machine body away from the engine 21 and at a position where maintenance work can be easily performed, and the counter. It can be installed at a position close to the case 25. The harness to be stretched between the travel controller 194 and the counter case 25 can shorten the extension distance, improve the assembling property and handling property, 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 bases 202 and 203 are disposed on the upper surface of the machine base 3 and the support base 23. The fastening seat 201 is fixed to the receiving bases 202 and 203 with bolts 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 from the opening 205 on the side surface of the support base 23. For example, there is no need to install the battery 206 by extending the machine base 3 on the front side of the threshing portion 4 forward. The machine base 3 can be used effectively and the maintenance work can be simplified.

  In addition, 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 laterally, the hydraulic valve set 197 is maintained when the grain tank 15 is rotated laterally. It will be easy to do. On the other hand, 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 base 3 and the fuel tank 207 on the rear side of the machine base 3. The exhaust pipe 208 can be set apart from the hydraulic valve set 197 and the like.

  Further, as shown in FIGS. 6 and 8, the 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, 24 is placed 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 an attachment member of the harness 210 or a reinforcement member of the support base 23.

  When the harness 210 of the speed change valve 211 is supported on the support frame 209, the support frame 209 can be used as a reinforcing member of the support base 23, and the harness 210 can be easily attached using the support frame 209. When the controller 194 of the speed change valve 211 is provided between the left and right support bases 23, 24, while the side rotation fulcrum 199 of the cutting part 7 is provided on one support base 23, the controller 194 is connected to the cutting part 7. Since the front surfaces of the support bases 23 and 24 opened by side rotation can be used for easy maintenance, the counter case 25 and the controller 194 can be brought close to each other.

  Further, as shown in FIGS. 4, 7, and 8, when the bracket 212 is installed on the front side of the transmission case 22 and the bracket 212 is fixed to the middle of the connection frame 34, the mounting height of the connection frame 34 with respect to the transmission case 22, Alternatively, restrictions such as the height of the accessory parts provided on the upper surface of the mission case 22 can be relaxed, and the structure of the mission case 22 and the airframe configuration can be simplified and the rigidity can be improved. Further, when the drain port 213 is provided on the upper surface of the mission case 22 and the air vent pipe 214 is connected to the drain port 213, the drain port 213 can be installed at a substantially highest position on the upper surface of the mission case 22. By connecting, the drain structure of the mission case 22 can be simplified.

  Furthermore, as shown in FIG. 21, on the input side of the work controller 282 constituted by a microcomputer, a threshing switch 272 for detecting the operation of the work lever 271 for driving the threshing part 4 and the reaping part 7 are driven. A cutting switch 273 for detecting the operation of the work lever 271 for switching, a cutting switch 274 for switching the cutting shift slider 155 to the low speed side or the high speed side, and a high speed operation switch 275 for detecting a high speed forward switching operation of the main transmission lever 81. A reverse switch 276 for detecting the reverse switching operation of the main transmission lever 81, a manual pouring switch 278 for detecting the stepping operation of the pouring pedal 277, an auxiliary shifting switch 279 for performing an auxiliary shifting (low speed or high speed), and cutting Auto lift switch 280 that automatically raises or lowers part 7 and discharge The auto set switch 281 that automatically turns the agar 17 from the storage position to the grain discharge position, left and right vehicle speed sensors 285 and 286 that detect the vehicle speed of the left and right traveling crawler 2, The grain culm sensor 287 to be detected is connected to the reaping input sensor 288 for detecting the input rotational speed of the tuning input shaft 112 for inputting the vehicle speed tuning driving force to the reaping part 7 via the low speed gear 152.

  Further, as shown in FIG. 21, on the output side of the work controller 282, a cutting low speed 289 for switching the cutting gear cylinder to the low speed side, a cutting high speed solenoid 290 for switching the cutting gear cylinder to the high speed side, and a feed chain clutch cylinder Is operated to turn off the feed chain clutch 131, a constant rotation cylinder is operated to cause the switching slider 124 to flow into the flow gear 123, and a constant rotation cylinder is operated to operate the constant rotation cylinder. 124 is connected to a high-speed cut solenoid 293 that engages with the high-speed cut gear 156. Further, as shown in FIG. 16, the tuning input shaft 112 is provided with a rotation sensor 301 for detecting the rotation speed for calculating the cutting input rotation speed, and the rotation of the tuning input shaft 112 detected by the rotation sensor 301. The cutting input rotation speed is calculated by the number and the gear tooth number. Note that a rotation sensor 302 for detecting the rotation speed for calculating the cutting input rotation speed can be installed on the cutting transmission shaft 125 so that the cutting input rotation speed is calculated.

  Next, FIG. 22 is a flowchart of speed control of the cutting unit 7, and FIG. 23 is a relationship between the cutting rotational speed KVx (driving speed of the cutting unit 7) of the cutting transmission shaft 125 for driving the cutting unit 7 and the vehicle speed SV. FIG. With reference to FIG.22 and FIG.23, the control which switches the drive speed of the cutting part 7 is demonstrated. When the cutting switch 273 is turned on (S1yes), the autolift switch 280 is turned on and the cutting unit 7 is lowered to the grain cutting height (S2yes), the cutting rotational speed KVx of the cutting transmission shaft 125 is changed to the low speed constant speed rotation Vq. Low speed constant speed control is performed (S3). In this low speed constant speed control, the cutting constant speed cylinder 143 is operated by the excitation of the flow solenoid 292. The switching slider 124 is switched by the mowing constant speed cylinder 143. The switching slider 124 is connected to the pouring gear 123. A low speed constant rotational force for driving the cutting transmission shaft 125 is transmitted from the casting gear 123 to the cutting transmission shaft 125. The cutting unit 7 is driven at the low speed and constant speed rotation Vq.

  On the other hand, when the main speed change lever 81 is operated so as to increase the vehicle speed SV and the harvesting operation is started while the low speed constant speed control (S3) is being performed, the vehicle speed sensors 285 and 286 When the input vehicle speed SV is increased to the vehicle speed qH corresponding to the lower return point Dt2 (S4 yes), vehicle speed synchronization speed control is performed (S5). In this vehicle speed synchronized speed control, the cutting constant speed cylinder 143 operates so as to return the switching slider 124 to neutral. The vehicle speed synchronized driving force output from the traveling motor 42 of the transmission case 22 is transmitted to the cutting transmission shaft 125 via the low speed gear 152 or the high speed gear 153. The driving speed in the cutting unit 7 is switched to a vehicle speed tuning speed that follows the vehicle speed tuning pattern that synchronizes with the vehicle speed SV and increases in proportion to the increase in the vehicle speed SV.

  When the vehicle speed synchronization speed control (S5) is being performed, the main transmission lever 81 is operated by the operator to slow down the vehicle speed SV, and the vehicle speed SV input from the vehicle speed sensors 285 and 286 is changed to the lower transition point. When the vehicle is decelerated to the vehicle speed tH corresponding to Dt (S6 yes), low speed constant speed control is performed to set the rotational speed KVx of the cutting transmission shaft 125 to the low speed constant speed rotation Vq (S7). The vehicle speed tH corresponding to the lower shift point Dt is the lower limit of the vehicle speed SV in the vehicle speed tuning section D. The rotational speed Vt of the cutting 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 Dt1 substantially the same as the lower return point Dt2.

  When the low speed constant speed control (S7) is performed, the cereals harvested by the reaping unit 7 are carried out to the threshing unit 4, and the cereals detected by the cereal sensor 287 disappear from the reaping unit 7. (S8no), stop control for stopping the cutting unit 7 is performed (S9). Both the cutting low-speed solenoid 289 and the cutting high-speed solenoid 290 are turned off, the low-speed gear 152 or the high-speed gear 153 is positioned in a neutral position, and the cutting unit 7 is stopped.

  When the vehicle speed synchronization speed control (S5) is being performed, the main transmission lever 81 is operated by the operator to increase the vehicle speed SV, and the vehicle speed SV input from the vehicle speed sensors 285 and 286 is changed to the upper shift point. When the vehicle speed is increased to the vehicle speed rH corresponding to Dr (S10 yes), high speed constant speed control is performed to set the cutting rotational speed KVx of the cutting power transmission shaft 125 to the high speed constant speed rotation Vrx (S11). In this high speed constant speed control, the cutting constant speed cylinder 143 is operated by excitation of the high speed cut solenoid 293. The switching slider 124 is switched by the mowing constant 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 cutting transmission shaft 125 is transmitted from the high speed cut gear 156 to the cutting transmission shaft 125. The speed rotation Vr of the cutting part 7 corresponding to the upper shift point Dr is switched to the high speed constant speed rotation Vrx corresponding to the first upper constant speed point Dr1, and the cutting part 7 is driven by the high speed constant speed rotation Vrx. become. 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.

  On the other hand, when the high speed constant speed control (S11) is being performed, the main speed change lever 81 is operated by the operator to slow down the vehicle speed SV, and the vehicle speed SV input from the vehicle speed sensors 285 and 286 is returned to the upper level. When the vehicle speed is decreased to the vehicle speed pH corresponding to the point Dr3 (S12 yes), vehicle speed synchronization speed control is performed (S5). In this vehicle speed synchronized speed control, the cutting constant speed cylinder 143 operates so as to return the switching slider 124 to neutral. The vehicle speed synchronized driving force output from the traveling motor 42 of the transmission case 22 is transmitted to the cutting transmission shaft 125 via the low speed gear 152 or the high speed gear 153. The driving speed in the cutting 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 tuned speed rotation Vry corresponding to the upper return point Dr3 to synchronize with the vehicle speed SV and increase the vehicle speed SV. Therefore, the vehicle speed is synchronized with the vehicle speed synchronization pattern that increases in proportion to the vehicle speed synchronization pattern.

  As shown in FIGS. 23 and 24, a vehicle speed tuning section D that is transmitted to the cutting transmission shaft 125 via the high speed gear 153 is formed. A vehicle speed tuning section E that is transmitted to the cutting transmission shaft 125 via the low speed gear 152 is formed. The upper and lower limits of the vehicle speed SV are different in the vehicle speed synchronization speed in each of the vehicle speed synchronization sections D and E. On the other hand, the range (Vr to Vt) of the vehicle speed synchronization speed corresponding to the vehicle speed SV in each vehicle speed synchronization section D, E, the low speed constant speed Vq of the cutting unit 7, and the high speed constant speed Vrx of the cutting unit 7 have the same value. Adopted.

  As is clear from the above, the driving speed KVx in the cutting unit 7 is synchronized with the vehicle speed SV and increases in proportion to the increase in the vehicle speed SV, regardless of the vehicle speed synchronization speed or increase / decrease in the vehicle speed SV. In a combine configured to drive the cutting unit 7 by switching to one of the substantially constant rotation speeds Vq and Vrx, the vehicle speed sensors 285 and 286 for detecting the vehicle speed SV and the cutting unit 7 are driven. A cutting input sensor 288 for detecting the rotational speed of the input shaft 112 for controlling the driving speed KVx of the cutting unit 7 is switched to one of the low speed constant speed Vq, the vehicle speed tuning speed, and the high speed constant speed Vrx. When the vehicle speed SV in the vehicle speed synchronization section D is decelerated to the lower shift point Dt, the driving speed of the reaping unit 7 is provided. While Vx is switched to the low speed constant speed Vq, when the vehicle speed SV is increased to the upper shift point Dr, the driving speed KVx of the cutting unit 7 is controlled to be switched to the high speed constant speed Vrx. .

  Therefore, when the vehicle speed SV in the vehicle speed tuning section D is decelerated to the lower shift point Dt, the driving speed KVx of the reaping section 7 is switched to the low speed constant speed Vq. By determining the vehicle speed tH of the lower shift point Dt so that it can be driven at a slow vehicle speed synchronization speed, the tip of the culm is handled in the pulling work of the reaping part 7 in the low-speed traveling harvesting work and shed. Can be prevented.

  On the other hand, when the vehicle speed SV is increased to the upper shift point Dr, the driving speed KVx of the cutting unit 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 it can be driven at a fast high speed constant speed Vrx, it is possible to prevent overloading in the high speed traveling harvesting operation.

  Therefore, in both the low-speed traveling harvesting operation and the high-speed traveling harvesting operation, the cutting unit 7 can be appropriately driven at the low-speed constant speed Vq or the high-speed constant speed Vrx. It is possible to improve the work efficiency of the high-speed traveling harvesting work.

  The low constant speed Vq is set higher than the driving speed KVx of the cutting unit 7 corresponding when the vehicle speed SV is the lower shift point Dt. When driving at a vehicle speed synchronization speed that follows the pattern, the vehicle speed in the vehicle speed synchronization section is temporarily close to the lower shift point Dt so that the drive speed KVx of the cutting unit 7 is lower than the low speed constant speed Vq. Even when the speed is reduced, the driving speed KVx of the cutting part 7 is maintained at the vehicle speed synchronization speed that follows the vehicle speed synchronization pattern, and the grain tip can be prevented from being shattered by being raised by the cutting part. .

  When the vehicle speed SV is increased by an appropriate value from the lower shift point Dt, the driving speed KVx of the cutting unit 7 that has once reached the low constant speed Vq returns to the lower return point Dt2 on the vehicle speed tuning pattern. Thereafter, the control means 282 switches the driving speed KVx to adopt the vehicle speed tuning speed on the vehicle speed tuning pattern, so that the vehicle speed qH at the lower return point Dt2 is changed to the vehicle speed tH at the lower shift point Dt. The driving speed KVx of the cutting unit 7 can be smoothly switched from the low speed constant speed Vq to the vehicle speed tuning speed according to the vehicle speed tuning pattern.

  The high speed constant speed Vrx is set higher than the driving speed KVx of the reaping portion 7 corresponding to the vehicle speed SV in the vehicle speed tuning section D corresponding to the upper shift point Dr. The driving speed KVx of the cutting unit 7 can be switched from the vehicle speed tuning speed along the vehicle speed tuning pattern to the high speed constant speed Vrx. When the cutting unit 7 is driven at a vehicle speed synchronization speed that follows the vehicle speed synchronization pattern, the cutting unit 7 can be smoothly shifted to the high-speed traveling harvesting operation that 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, after the driving speed KVx of the cutting unit 7 that has once reached the high speed constant speed Vrx returns to the upper return point Dr3 on the vehicle speed tuning pattern. Since the control means 282 switches the driving speed KVx to adopt the vehicle speed tuning speed on the vehicle speed tuning pattern, the vehicle speed pH of the higher return point Dr3 is set to be higher than the vehicle speed rH of the higher shift point Dr. In addition, the driving speed KVx of the cutting unit 7 can be smoothly switched from the vehicle speed tuning speed along the vehicle speed tuning pattern to the high speed constant speed.

  The control means 282 controls the driving speed KVx of the reaping portion 7 so as to switch from the vehicle speed synchronization speed to the low speed constant speed Vq when moving backward. At the time of reverse travel, the cutting unit 7 is in a stopped state, so even if the cutting unit 7 is driven from a stopped state, the driving of the cutting unit 7 is started at a low constant speed Vq. The impact load when starting the driving of the cutting unit 7 can be suppressed.

  Next, information display and control by CAN communication will be described with reference to FIGS. As shown in FIG. 25, the work controller 282 in FIG. 21 includes a column controller 350 and a travel controller 351. An engine controller 352 that controls the engine 21, a column controller 350, and a travel controller 351 are configured to be connected by a CAN cable 353. Note that a cutting position sensor 354 that detects the lift position of the cutting unit 7 is disposed on the input side of the travel controller 351.

  On the other hand, to the output side of the column controller 350, a general display liquid crystal panel 355 disposed 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 contents of the liquid crystal panel 355, and a setting switch for selecting the first selection switch 356 and the second selection switch 357 are provided. 358 and a determination switch 359 for determining the display content of the liquid crystal panel 355 are configured to be connected to each other.

  As shown in FIG. 26, when the first selection switch 356, the second selection switch 357, and the setting switch 358 are operated to switch the display content of the liquid crystal panel 355 to an error display, an error code (for example, CO-320) is displayed. The error location (for example, engine oil temperature sensor, engine room, engine controller) is displayed on the liquid crystal panel 355.

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

  On the other hand, as shown in the flowchart of FIG. 28, the cutting unit 7 is operated at a low constant speed (pour) speed, a high speed constant (high speed cut) speed, or a vehicle speed synchronization speed, and the hydraulic travel speed change member is moved from the counter case 25. A constant rotational force is transmitted to the motor shaft 46 of the 40 traveling motor 39, and the traveling crawler 2 is directly driven at a higher rotational speed 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 sub speed change cylinder is switched by switching the high speed operation solenoid 295 for turning on the bypass clutch and the sub speed change switch 279. A sub-transmission solenoid 296 for driving to drive the traveling motor 39 at low speed or high speed, a threshing clutch solenoid 297 for turning on the threshing clutch 97 when the threshing switch 272 is turned on, and the auto lift switch 280 A mowing elevating solenoid 298 for moving the elevating cylinder 11 up or down when turned on, and a discharge motor 299 for moving the discharge auger 17 to the grain discharging position or the machine storage position when the autoset switch 281 is turned on. Are connected to the work controller 282.

  As described above, the pouring pedal 277, which is a pouring operation member that performs the pouring operation for carrying the cereal of the mowing unit 7 to the threshing unit 4, is provided, and the pouring unit 7 that operates in synchronization with the vehicle speed is different from the tuning rotational speed. In the combine driven by the rotational speed of the operation, the casting gear 123 and the high-speed cut gear 156 that cause the reaping section 7 to perform the pouring operation are selected based on the rotational speed of the driving input for the vehicle speed synchronization of the reaping section 7 when the pouring pedal 277 is operated. Then, the rotational speed of the drive input of the cutting unit 7 is selected. Then, the problem that the driving speed of the cutting unit 7 greatly changes when the pouring operation is started using the pouring gear 123 is eliminated, and the pouring operation is performed using the high speed cut gear 156 without making the operator feel uncomfortable. It will be.

  In addition, a cutting input sensor 288 that detects the rotational speed of the driving input for the vehicle speed synchronization of the cutting unit 7 is provided, and when the flow pedal 277 is operated, the input rotational speed for the vehicle speed synchronization of the cutting unit 7 is poured by the flow gear 123. In the following case (when the rotation speed is lower than the casting rotation speed by a certain number of rotations), the casting solenoid 292 is turned on and the casting rotational power is continued through the casting gear 123.

  On the other hand, when the rotational speed of the cutting unit 7 is equal to or higher than the casting rotational speed of the pouring gear 123 (more than a certain rotational speed higher than the casting rotational speed), the high speed cutting solenoid 293 is turned on and the high speed cutting gear 156 is rotated at high speed. By continuing the power and setting the pouring rotational power by the pouring gear 123 to the low speed side, the pouring gear 123 starts operating smoothly with a smaller speed difference than the conventional one, and even under high speed cutting conditions, the high speed cut gear The cutting part 7 is operated at the highest speed by the pouring operation by 156, and the conventional uncomfortable feeling that the cutting speed is reduced is eliminated.

  In addition, a tuning input shaft 112 which is a driving system path for vehicle speed tuning, a pouring gear 123 which is a driving system path for pouring, and a high speed cut gear 156 which is a high speed side constant speed rotational driving system path for high speed side constant rotation. Select one of them to drive the cutting unit 7 and rotate the cutting unit 7 at a constant speed to perform the cutting operation to perform the pouring operation at the highest speed to simplify the cutting drive structure. Improve mowing drive performance.

  On the other hand, a cutting transmission mechanism 151 is provided on the input path of the tuning input shaft 112 that drives the cutting unit 7, the cutting transmission mechanism 151 is kept neutral to stop power transmission, and the cutting unit 7 is connected to the gears 123 and 156. The driving crawler 2 is driven by the motor shaft 46 of the traveling motor 39 when the pouring operation is performed by turning on or off the driving force synchronized with the vehicle speed by using the cutting transmission mechanism 151 as a cutting clutch. The power loss is reduced, the cutting drive structure is simplified, and the driving efficiency of the traveling crawler 2 is improved.

  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 cutting unit 7 is rotated at a constant speed higher than the vehicle speed synchronization speed. When the vehicle speed tuning control is in progress when the cutting speed is high, and the vehicle speed SV is equal to or higher than the vehicle speed a, high speed constant rotation control is performed to rotate the cutting unit 7 at a speed higher than the vehicle speed synchronization speed. On the other hand, when the vehicle speed SV is not equal to or higher than the vehicle speed a, vehicle speed synchronization control is performed.

  On the other hand, when the cutting speed is high, the vehicle speed synchronization control is not being performed. 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 less than the vehicle speed b, high speed constant rotation control is performed to rotate the cutting unit 7 at a speed higher than the vehicle speed synchronization speed.

  When the cutting speed is not high and the vehicle speed tuning control is in progress, if the vehicle speed SV is equal to or higher than the vehicle speed c, the high speed constant rotation control is performed to rotate the cutting portion 7 at a speed higher than the vehicle speed tuning speed. . On the other hand, when the vehicle speed SV is not equal to or higher than the vehicle speed c, vehicle speed synchronization control is performed.

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

  As shown in the flowchart of FIG. 30 and the output diagram of FIG. 31, mowing quick control for rotating the mowing unit 7 at a constant speed corresponding to the present invention described in the claims will be described. When the pouring pedal 277, which is a mowing quick pedal, is stepped on and the pouring switch 278 is turned on, the piping section 7 is driven when moving forward, the mowing speed is high, and the vehicle speed SV is equal to or higher than the vehicle speed a. The harvesting quick “high” control is performed in which the speed is driven at a constant rotation at a high speed higher than or equal to the vehicle speed synchronization speed. On the other hand, when the vehicle speed SV is not equal to or higher than the vehicle speed a, the cutting quick drive “low” control is performed in which the driving speed of the cutting unit 7 is driven to rotate at a constant speed at a low speed lower than or equal to the vehicle speed synchronization speed.

  On the other hand, when the vehicle is moving forward and the cutting speed is not high, when the vehicle speed SV is equal to or higher than the vehicle speed b, the cutting operation is performed so that the driving speed of the cutting unit 7 is driven to rotate at a high speed side of the vehicle speed synchronization speed or higher. You will have quick “high” control. On the other hand, when the vehicle speed SV is not equal to or higher than the vehicle speed b, the cutting quick drive “low” control is performed in which the driving speed of the cutting unit 7 is driven to rotate at a constant speed at a low speed lower than or equal to the vehicle speed synchronization speed.

  When the vehicle is not moving forward, the cutting portion 7 is controlled to perform the quick cutting “low” for constant rotation at a low speed side of the vehicle speed synchronization speed or a lower speed.

  Further, when the pouring pedal 277, which is a mowing quick pedal, is not stepped on and the pouring switch 278 is turned off, and the mowing speed is high, the driving speed of the mowing section 7 is set to the mowing speed “high”. Tuning control will be performed. On the other hand, when the cutting speed is low, the driving speed of the cutting unit 7 is controlled to be synchronized with the cutting speed “low”.

  As is apparent from the above, the flow rate sensor 285, 286 for detecting the vehicle speed, and the casting means which is a switching means for switching the driving speed of the cutting unit 7 to one of the low speed constant speed, the vehicle speed tuning speed, or the high speed constant speed. Since the pedal 277 is provided, it is possible to prevent the grain tip from being handled and shattered in the raising operation of the harvesting part in the low-speed traveling harvesting operation. On the other hand, it is possible to prevent an overload in a high-speed traveling harvesting operation. Therefore, the harvesting unit 7 can be properly driven at the low speed constant speed or the high speed constant speed at any time of the low speed traveling harvesting work or the high speed traveling harvesting work, thereby improving the harvesting workability of the low speed traveling harvesting work. In addition, the working efficiency of high-speed traveling harvesting work can be improved.

  The low speed constant speed is set to be higher than the corresponding driving speed of the cutting unit 7 when the vehicle speed in the vehicle speed tuning section is a lower shift point for switching the driving speed of the cutting unit 7 to the low speed constant speed. Therefore, when the cutting unit 7 is driven at a vehicle speed tuning speed that follows the vehicle speed tuning pattern, the vehicle speed tuning is performed so that the driving speed of the cutting unit 7 is lower than the constant low speed. Even if the vehicle speed in the section is temporarily decelerated to near the lower shift point, the driving speed 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 cereal is raised by the cutting unit 7. It can be prevented from being shattered by handling.

  The high speed constant speed is set to be higher than the driving speed of the cutting unit 7 corresponding to the vehicle speed in the vehicle speed synchronization section when the driving speed of the cutting unit 7 is an upper shift point for switching to the high speed constant speed. Therefore, the driving speed of the cutting 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 in the output of the engine 21. When the cutting unit 7 is driven at a vehicle speed synchronization speed that follows the vehicle speed synchronization pattern, the cutting unit 7 can be smoothly shifted to the high-speed traveling harvesting operation that drives at the high-speed constant speed. Efficiency can be improved.

  The switching means 277 controls the driving speed of the cutting unit 7 to be switched from the vehicle speed synchronization speed to a low constant speed when the switching means 277 is switched when moving backward. At the time of reverse travel, the cutting unit 7 is in a stopped state. Therefore, even when the cutting unit 7 is driven from a stopped state, the driving of the cutting unit 7 is started at a low constant speed. The impact load at the start of the driving of the cutting unit 7 can be suppressed.

  In addition, the cutting unit 7 is driven at a vehicle speed-synchronized drive that changes the cutting speed in synchronization with the vehicle speed or a constant-speed casting driving speed that keeps the cutting speed substantially constant, while the constant-speed casting driving speed is set to a high speed and a low speed. Since the cutting part 7 is driven at the constant speed driving flow speed at a high speed or a low speed, either the low speed traveling harvesting work or the high speed traveling harvesting work is performed. However, the cutting unit 7 can be driven appropriately at the low speed constant speed or the high speed constant speed, and the cutting efficiency of the low speed traveling harvesting work can be improved, and the working efficiency of the high speed traveling harvesting work can be improved.

  In addition, since the vehicle speed tuning speed of the cutting unit 7 for switching from the vehicle speed synchronized driving to the constant speed driving driving speed on the high speed side is made lower than the constant speed driving driving speed on the low speed side, The driving speed of the cutting unit 7 is increased by the operator's switching operation over the entire vehicle speed synchronization speed of the unit 7, and the operator can operate without discomfort.

  The harvesting operation control will be described with reference to the flowchart of FIG. When the threshing switch 272 is turned on by the operation of the operation lever 271, the feed chain solenoid 291 is turned off to turn on the feed chain clutch 131, the drive of the feed chain 5 is started, and the threshing clutch solenoid 297 is operated to operate the threshing clutch. 97 is turned on, and the threshing unit 4 and the feed chain 5 are driven.

  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, if the pouring operation of the pouring pedal 277 is performed and the pouring switch 278 is turned on, the mowing input sensor 288 detects the cutting speed when the input rotational speed of the mowing portion 7 is equal to or less than the rotation setting by the pouring gear 123. The shift slider 155 is moved to the neutral position, the cutting shift output of the cutting transmission 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, via the pouring gear 123. The mowing unit 7 is driven at a constant speed at a lower speed than the high speed cut gear 156.

  On the other hand, when the pouring switch 278 is turned on, if the input rotational speed of the trimming unit 7 is equal to or higher than the rotation setting by the pouring gear 123, the trimming shift output of the trimming transmission mechanism 151 is made neutral, and the tuning input shaft 112 And the high speed cut solenoid 293 operates to drive the cutting unit 7 through the high speed cut gear 156 at a constant speed at a maximum speed higher than that of the flow-in gear 123.

  Further, when the auto-lift switch 280 is turned on when the pouring switch 278 is off, the cutting gear shift output of the cutting gear shift mechanism 151 is neutralized, and when the ground height of the cutting unit 7 is equal to or lower than the setting, the lifting cylinder 11 is moved. Actuate to automatically raise the cutting unit 7 to the set height and to turn off the feed chain clutch 131. On the other hand, when the ground height of the cutting unit 7 is equal to or higher than the set value, the lifting cylinder 11 is controlled to automatically lower the cutting unit 7 to the cutting work height, and the feed chain clutch 131 is turned on.

  If the reverse switch 276 is turned on when the autolift 280 is off, the cutting gear shift output of the cutting gear shift mechanism 151 is neutralized, the solenoids 292 and 293 are turned off, and the switching slider 124 is neutralized. Become.

  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 made neutral and the vehicle speed synchronized driving of the cutting unit 7 is stopped. On the other hand, when the axle 55 is driven, the input rotation for the vehicle speed synchronization of the cutting unit 7 detected by the cutting input sensor 288 is greater than or equal to the rotation setting by the high speed cut gear 156 when the sub-shift output of the transmission motor 39 is low. At this time, the high-speed cut solenoid 293 is operated, the cutting transmission mechanism 151 is made neutral, and the high-speed cutting operation for driving the cutting unit 7 at the maximum speed through the high-speed cutting gear 156 is performed.

  Further, when the high-speed operation switch 275 is turned on when the sub-shift output of the transmission motor 39 is low speed, the input rotation of the cutting unit 7 is less than the setting, and the automatic switch 284 is on, the input of the cutting unit 7 is performed. In a state where the rotation is equal to or higher than the set value, the cutting unit 7 is rotated at a constant speed at the highest speed via the high speed cut gear 156 and the high speed cutting operation is performed as described above. In addition, the high-speed operation solenoid 295 is operated to turn on the bypass clutch, and the driving force of the engine 21 is directly transmitted from the bypass clutch to the sub-transmission mechanism 47 without using the traveling speed change member 40 to perform high speed operation.

  Further, when the high speed operation switch 275 is off, the cutting shift output of the cutting transmission mechanism 151 is switched to low speed or high speed by operating the cutting shift switch 274. The cutting unit 7 is driven at a low speed or a high speed by a vehicle speed tuning input through one of the gears 152 and 153. The standing culm is cut at a low speed or the lying cereal is harvested at a high speed.

  As shown in FIG. 24, the cutting unit 7 is driven at a constant speed at a low speed or a high speed via the pouring gear 123 or the high speed cut gear 156 by the quick mowing operation of the pouring pedal 277 during the mowing operation synchronized with the normal vehicle speed. In this case, the working speed when switching to the high-speed cutting that is driven at a high speed and the constant speed is made different from the working speed when releasing this switching. Due to the output from the low speed gear 152 (or the high speed gear 153) of the cutting transmission mechanism 151, the working speed (the rotational speed of the tuning input shaft 112) is equal to or higher than the vehicle speed a (or vehicle speed b) in the cutting shift (high speed or low speed) state. In this case, the driving of the cutting unit 7 is switched to high speed cutting (high speed and constant speed driving).

  Further, when the cutting quick operation is canceled, the high speed cut is maintained when the operating speed is reduced until the operating speed of the high speed cutting cancellation value that is smaller than the high speed cutting of the cutting driving speed reaches the vehicle speed c (or the vehicle speed d). . When the work speed becomes the vehicle speed c (or the vehicle speed d), the driving of the cutting unit 7 is returned to the normal shift.

Claims (6)

The driving speed in the cutting part is either the vehicle speed synchronization speed that follows the vehicle speed synchronization pattern that synchronizes with the vehicle speed and increases in proportion to the increase in the vehicle speed, or a substantially constant rotation speed that is set in advance regardless of the increase or decrease of the vehicle speed. In a combine configured to switch and drive the reaping part,
A vehicle speed sensor for detecting the vehicle speed;
A combine comprising switching means for switching the speed in the driving vehicle speed tuning section of the mowing unit to either a low speed constant speed, a vehicle speed tuning speed, or a high speed constant speed. The low speed constant speed is set higher than the driving speed of the corresponding cutting part when the vehicle speed in the vehicle speed synchronization section is a lower shift point for switching the driving speed of the cutting part to the low speed constant speed. The combine according to claim 1. The high speed constant speed is set to be higher than the driving speed of the cutting part corresponding to the time when the vehicle speed in the vehicle speed tuning section is an upper shift point for switching the driving speed of the cutting part to the high speed constant speed. The combine according to claim 1 or 2, characterized in that 2. The switching device according to claim 1, wherein when the switching device is switched, the driving speed of the cutting unit is controlled so as to switch from a vehicle speed synchronization speed to a low constant speed. 3. Combine according to 3. The cutting part is driven at a vehicle speed synchronous drive that changes the cutting speed in synchronism with the vehicle speed or at a constant speed casting drive speed that keeps the cutting speed substantially constant, while the constant speed casting driving speed is set to a high speed and a low speed 2 2. The combine according to claim 1, wherein the combiner is configured to switch to a stage and to drive the mowing unit at the constant or constant flow driving speed. 5. The vehicle speed tuning speed of the cutting unit for switching from the vehicle speed tuning drive to the constant speed driving driving speed on the high speed side is configured to be lower than the constant speed driving driving speed on the low speed side. Combine as described.

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