KR20050042799A - Combine - Google Patents

Abstract

A combine for driving a traveling section (2) by transmitting the power of an engine (21) to a transmission case (22) provided with a traveling speed change mechanism (40), characterized in that the power of the engine (21) is transmitted to a counter case (25) in order to drive a threshing section (4) by a substantially constant rotational output and the speed change output from the traveling speed change mechanism (40) is transmitted to the counter case (25) in order to drive a reaping section (7) at a speed synchronous with the vehicle speed, and the counter case (25) is arranged such that the reaping section (7) is driven at a substantially constant speed by a substantially constant rotational output from the counter case (25). The counter case (25) for driving the threshing section (4) at a constant speed can also drive the reaping section (7) at a speed synchronous with the vehicle speed or at a substantially constant speed, and the reaping section (7) can be driven at a constant speed utilizing a part of the driving system of the threshing section (4), resulting in simplification of driving structure of the reaping section (7), or the like and reduction of transmission loss.

Description

Combine {COMBINE}

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

Conventionally, for example, as shown in Japanese Patent Laid-Open No. 62-163826, in a combine or the like equipped with a left and right traveling crawler, the traveling portion (driving crawler) is driven by the shift output of the hydraulic pump of the hydraulic transmission mechanism at the maximum speed. ), And at the maximum speed, the input and output sides of the hydraulic transmission mechanism are directly connected by the constant speed mechanism, which leads to a problem of being operated by the output of the maximum speed of the hydraulic transmission mechanism that is unstable and has high horsepower. Even when switching from the output of the sphere to the output of the constant speed mechanism, there is a problem that the speed does not increase and the improvement of the driving performance cannot be easily achieved. In addition, there is a problem that shock is likely to occur due to a rotation difference (speed difference) before and after being directly connected by the constant speed mechanism, and when driving the driving part by the constant speed output of the constant speed mechanism, for example, hydraulic power transmission. In the hydraulic transmission mechanism having uneven characteristics, it is difficult to match the discharge amounts of the hydraulic pump and the motor, and there is a problem of effectively recovering the lost horsepower or increasing the load. There is a problem that the simplification and the reduction of the transmission loss cannot be easily performed.

1 is a perspective view of a combine.

2 is a side view of the same.

3 is an explanatory view of the same plane.

4 is a side explanatory diagram of the front body.

5 is an explanatory front view of the same.

6 is an explanatory view of the side of the drive unit.

7 is a front explanatory diagram of the same.

8 is an explanatory view of the same plane.

9 is a drive system diagram of the transmission case.

10 is a plan view of the same.

11 is the same cross-sectional back view.

12 is an enlarged view of the front view.

FIG. 13 is an enlarged view.

14 is an engine power system diagram.

15 is a hydraulic circuit diagram.

16 is a drive system diagram of the counter case.

17 is a plan view of the same cross section.

18 is an enlarged view.

19 is the same cross-sectional side view.

20 is an external appearance front view.

21 is a plan view of the same.

22 is the same side view.

23 is a plan view of the threshing clutch portion.

24 is the same rear view.

25 is the partial view.

26 is a cross-sectional view of the threshing cylinder portion.

27 is a bottom view of the flow path base.

28 is a cross-sectional side view of the same.

29 is a cross-sectional view of the mowing shift cylinder portion.

30 is a cross-sectional view of the mowing constant speed cylinder portion.

31 is a cross sectional rear view of the fork shaft part.

32 is an explanatory diagram.

33 is a control circuit diagram.

34 is a harvest control flow chart of the previous view.

35 is a homogeneous speed control flow chart.

36 is a driving pump output line.

FIG. 37 is a drive system diagram of a counter case showing the modified structure of FIG.

38 is a cross-sectional view of the constant speed clutch portion of FIG.

The present invention provides a combiner that transmits power of an engine to a transmission case provided with a traveling transmission mechanism to drive a running unit, wherein the engine power is transmitted to a counter case, and the threshing unit is driven by a substantially constant rotational output. The counter case is configured to transmit the shift output of the traveling transmission mechanism to the counter case to drive the harvesting section at a speed that synchronizes with the vehicle speed, and to drive the harvesting section at approximately constant speed by an approximately constant rotational output of the counter case. By using the counter case for driving the threshing portion at constant speed, the harvesting portion can be driven at either vehicle speed tuning or at about a constant speed, and the mowing portion can be configured to drive the harvesting portion at constant speed using a part of the drive system path of the threshing portion. Simplifies the drive structure of the harvesting section and reduces the electric loss. You can do it.

In addition, when the transmission output of the traveling transmission mechanism is near the highest speed, the approximately constant rotational output is transmitted to the output of the traveling transmission mechanism almost the same as when the transmission efficiency of the traveling transmission mechanism is the highest. Even if the power transmission efficiency of the sphere is lowered, the driving speed of the running section can be prevented from being lowered, so that the driving speed of the harvesting section can be properly maintained, and the high speed operation of increasing the load can be stably performed, for example, the harvesting straw is conveyed. Problems such as clogging on the way can be reduced, and the driving structure can be simplified and the transmission loss can be reduced.

In addition, at a speed equal to or shorter than the maximum speed, the driving unit is driven by the shift output of the hydraulic traveling pump and the traveling motor of the traveling transmission mechanism, and the output side of the traveling transmission mechanism is connected by the constant speed mechanism near the highest speed, and the traveling transmission is The hydraulic drive motor of the sphere has a variable output structure, and before the constant speed mechanism is connected, for example, the output variable of the hydraulic drive motor is fixed substantially constant at a low speed side, and the output of the hydraulic drive motor is variable. Although the transmission range can be expanded, there is a problem that the output of the traveling transmission mechanism tends to be unstable. Therefore, when the driving unit (and the work unit) starts to be driven by the output of the traveling transmission mechanism, the output of the hydraulic traveling motor is approximately constant. Therefore, the output of the hydraulic traveling pump is varied so that the output of the traveling transmission mechanism can be stabilized. As a result, driving of the traveling portion (and the working portion) can be started, the driving structure can be simplified, the driving loss can be reduced, and the driving operation and the handling can be improved.

When the output variable of the hydraulic traveling motor is made free by output operation of the constant speed mechanism, and the output side of the hydraulic traveling motor is directly connected when the input side of the hydraulic running pump and the output side of the hydraulic running motor are free, the hydraulic driving is made free. According to the discharge amount on the pump side, the hydraulic driving motor is adjusted by the hydraulic load or the like so that the main circuit hydraulic pressure is the lowest, so that the discharge amounts of the hydraulic driving pump and the traveling motor can be easily matched, and occupy the hydraulic pressure of the main hydraulic circuit ( It is possible to smoothly lower the charge) pressure, effectively recover the lost horsepower of the traveling transmission mechanism, simplify the drive structure, reduce the transmission loss, and the like.

In addition, the feed chain is provided with the threshing part, the feed chain transmission mechanism is installed in the counter case, and the feed chain is driven at a speed synchronized with the vehicle speed through the feed chain transmission mechanism. Can be kept relatively constant, and the good conveying water performance of the mowing straw can be easily ensured, and the mowing drive structure can be simplified, and the electric power loss can be reduced.

In addition, the feed chain is driven by a substantially constant rotational output of the counter case to secure the driving speed on the low speed side, and the feed chain is driven at a speed that is synchronized with the vehicle speed on the higher speed side than the above-mentioned approximately constant low speed driving speed. It is possible to change the driving speed of the feed chain in proportion to the speed of mowing operation while securing the minimum speed necessary for conveying straw, for example, to reduce problems such as clogging of mowing straw during transportation, and to drive structure. It is possible to simplify and reduce the transmission loss.

Best Modes for Carrying Out the Invention Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a complete perspective view of the combine, FIG. 2 is a right side view of the combine, and FIG. 3 is a plan explanatory view, in which 1 is a pair of left and right track frames on which a pair of left and right traveling crawlers 2 are mounted, and 3 is the left and right track frames. Threshold part 4 which hangs on (1) and is a threshing part which is a threshing machine which feeds the feed chain 5 to the left side, and has built-in the barrel 6 and the process cylinder. , 7 is a cutting unit having a raising mechanism 8 and a cutting blade 9 and a straw conveying mechanism 10, etc., 11 is a hydraulic lifting cylinder for elevating the cutting unit 7 through the cutting frame 12, 13 The discharge straw processing unit having the end of the silver discharge straw chain 14 positioned, 15 is a grain tank carrying the grain from the threshing unit 4 through the grain barrel, and 16 and 17 are outside the grain of the tank 15. Exhaust auger to be transported to the outside, 18 is a driving cabin provided with a driving handle 19 and a driver's seat 20, 21 is a luck An engine installed on the lower cabin 18, and is configured to take threshing example continuously straw.

4 to 8, the transmission case 22 is provided between the left and right traveling crawlers 2 in front of the base 3, and the transmission case 22 and the engine 21 are roughly connected. It is installed before and after in series, and transmits the driving force of the engine 21 to the traveling crawler 2 via the transmission case 22, and supports left and right on the upper surface of the base 3 on the front side of the threshing part 4 24 is provided, and the harvesting | reaping part 7 is provided in the support stand 23 * 24 via the harvesting frame 12 so that the lifting and lowering part can be moved up and down horizontally. In addition, the counter case 25 is provided on the upper surface of the base 3 behind the support 23. 24, and the driving force of the engine 21 is applied to the threshing portion 4 and the harvesting portion 7 through the counter case 25. Tell.

In addition, the front frame 26 of the cabin is placed in the base 3 on the side of the transmission case 22, and the pivot point axis (in front of the front frame 26 of the step frame 27 of the cabin 18) is rotated. 28, and while supporting the cabin 18 to be able to rotate forward around the point shaft 28, the left cabin rear frame 29 is placed in the right support 24, The engine 21 is provided on the upper surface of the base 3 between the frame 30 on the right side of the base 3 to be placed in the base 3, and the engine 21 is covered with the engine room cover 31. In addition, the upper left and right rear frames 29 · 30 are connected by the cabin transverse frame 32 above the cover 31, and the Fuku lever 33 is provided on the cabin transverse frame 32, and the cabin ( The rear of the step frame 27 of 18) is placed on the transverse frame 32 so as to be fixed by the fuku lever 33 so that it can be pulled out and removed, and is horizontal between the support 24 on the right side and the front frame 26. The connecting frame 34 is fixed, and the inclined connecting frame 35 is fixed in the middle of the horizontal connecting frame 34 and the horizontal frame 32 to secure the frame rigidity by the connecting frame 34 · 35. In addition, the auger strut 36 is connected to the rear frame 29 on the left side to install the auger 37 at the upper side, and the auger auger 17 is installed to be lifted and turned. Support at 37) the machine storage position.

9 to 14, the transmission case 22 for driving the traveling crawler 2 is provided with a pair of hydraulic traveling pump 38 and hydraulic traveling motor 39 to travel around. The turning member 43 which forms the hydraulic continuously variable transmission mechanism which forms the hydraulic continuously variable transmission mechanism for speed, and a pair of hydraulic turning pump 41 and the hydraulic turning motor 42, and forms the hydraulic continuously variable transmission mechanism for turning. And the pumps 38 and 41 are connected to the output shaft 44 of the engine 21 via the input shaft 45 of the transmission case 22.

Further, the drive shafts 49 of the left and right traveling crawlers 2 are interlocked with each other via the sub transmission mechanism 47 and the differential mechanism 48 to the motor shaft 46 of the traveling motor 39. In other words, the differential mechanism 48 has a pair of left and right symmetric planetary gear mechanisms 50, and each planetary gear mechanism 50 has one sun gear 51 and an outer circumference of the sun gear 51. And three planetary gears 52 engaged with each other, and ring gears 53 engaged with these planetary gears 52, for example.

The planetary gear 52 is rotatably supported by the idling shaft 54 of the sun gear 51 and the carrier 56 of the axle 55 on the coaxial line, respectively, to sandwich the left and right sun gear 51. In addition to displacing the left and right carriers 56, the ring gear 53 has an inner tooth engaged with each planetary gear 52, and is rotatably supported on the axle 55, so that the axle 55 Is extended to support the driving wheel 49 axially.

In addition, the traveling transmission member 40 controls the forward and reverse rotation and the rotation speed of the traveling motor 39 by changing the inclination plate angle of the traveling pump 38, thereby rotating the traveling motor 39. Is transmitted to the left and right ring gears 53 through the low and high speed gears 57 and 58 of the motor shaft 46 and the sub transmission mechanism 47, the brake shaft 59, and the branch shaft 60. The left and right carriers 56 are configured to rotate. Further, a parking brake 61 is provided on the brake shaft 59, and a mowing drive pulley 62 for transmitting rotational force to the mowing part 7 is provided on the motor shaft 46, and a mowing part ( Drive 7 at vehicle speed tuning speed.

As described above, the driving force of the traveling motor 39 transmitted to the ring gear 53 through the branch shaft 60 is transmitted to the left and right carriers 56 through the left and right planetary gear mechanism 50. And the rotation transmitted to the left and right carriers 56 are transmitted to the left and right driving wheels 49, respectively, and the left and right traveling crawlers 2 are configured to be driven at the same speed in the same direction.

Moreover, the turning member 43 formed by the hydraulic continuously variable transmission mechanism for turning turns the forward rotation of the turning motor 42 and control of rotation speed by changing the inclination plate angle of the turning pump 41, and steering output The motor shaft 64 for providing the brake 63, the clutch shaft 66 for providing the steering output clutch 65, and the left and right input gears 67 and 68 which are always engaged with the left and right sun gears 51 described above. And the clutch shaft 66 is connected via the motor shaft 64 and the steering output clutch 65 for output of the turning motor 42, and the electrostatic gear 69 is connected to the clutch shaft 66. And the left and right input gears 67 and 68 via the reversing gear 70. Then, the rotation force of the motor 42 is transmitted to the sun gear 51 on the right side via the electrostatic gear 69, and the rotation of the motor 42 is transmitted to the sun gear 51 on the left side via the reverse gear 70. When the swing motor 42 is blackouted (reversed), the left gear 51 is reversed (reversed) at the same left and right rotation speeds, and the right gear 51 is blacked out (reversed). Is configured to drive at the same speed in the reverse direction.

However, when the traveling motor 39 is driven while the turning motor 42 is stopped and the left and right sun gears 51 are stationary fixed, the rotation of the traveling motor 39 is equal to the rotational speed of the left and right ring gears 53. And the traveling crawler 2 on the left and right are driven at the same rotational speed in the right and left same rotational directions via the carrier 56 of the left and right planetary gear mechanism 50, so that the vehicle travels in the forward and backward direction. On the other hand, when the turning motor 42 is driven forward and reverse with the driving motor 39 stopped and the left and right ring gears 53 stationary fixed, the planetary gear mechanism 50 on the left side is forward or reverse rotation, and The planetary gear mechanism 50 on the right side reverses or rotates forward, drives the left and right traveling crawler 2 in the reverse direction, and turns the body to the left or right. In addition, by driving the turning motor 42 while driving the traveling motor 39, the gas turns left and right so that the course is corrected, and the turning radius of the gas is determined by the output rotation speed of the turning motor 42. .

In addition, the fan shaft 71 is connected to the input shaft 45 to drive the cooling fan 72 of the radiator for water cooling of the engine 21 by the fan shaft 71, and the above traveling and turning pump 38 The fan shaft 71 is connected to each of the pump shafts 73 and 74 via the gear group 75 to connect the input shaft 45 to the pumps 38 and 41, and the traveling pump ( The constant speed shaft 77 which connects the pump shaft 73 of 38 and the motor shaft 46 of the traveling motor 39 via the constant speed clutch 76 was provided, and the constant speed clutch 76 was operated. At this time, the pump shaft 73 and the motor shaft 46 are gear-connected via the constant speed shaft 77, and the rotation of the input shaft 45 is rotated without interposing the traveling transmission member 40. And the traveling crawler 2 on the left and right by the constant speed rotation of the engine 21 to travel at a substantially constant vehicle speed to perform a harvesting operation or the like. Moreover, the charge pump 78 is provided and driven on the turning pump shaft 74.

Moreover, as shown in FIG. 15, it is connected to the main gear cylinder 80 which changes the angle of the inclination plate 79 of the traveling pump 38, and adjusts the output, and the main gear lever 81 and the steering wheel 19, A shift valve 32 for switching and a valve 83 for decelerating the output of the traveling pump 38 by a predetermined amount are provided, and the charge pump 78 is connected to the peripheral speed cylinder 80 via the valves 82 and 83. Hydraulically connected to the gearbox, the gearshift valve 32 is switched by the main gear lever 81, the main gear cylinder 80 is operated to change the angle of the inclination plate 79 of the travel pump 38, and the traveling motor ( Feedback operation in which the speed change operation of changing the rotation speed of the motor shaft 46 in step 39 or reversing steplessly is performed, and the shift valve 82 is neutrally returned by the angle adjustment operation of the inclined plate 79. To change the angle of the inclined plate 79 in proportion to the operation amount of the main gear lever 81 The vehicle speed is changed by changing the rotation speed of the travel motor 39.

Furthermore, the sub transmission cylinder 85 which changes the angle of the inclination plate 84 of the traveling motor 39, and adjusts an output is provided, and the secondary transmission cylinder () is provided to the said charge pump 78 via the electromagnetic sub transmission valve 86. 85 is hydraulically connected, and when the sub transmission valve 86 is neutral, the sub transmission cylinder 85 is shorted to the transmission case 22 which is an oil tank, and the angle of the inclined plate 84 of the traveling motor 39 is adjusted to the main circuit. In addition to changing by hydraulic pressure, the angle of the inclined plate 84 is forcibly changed by switching of the sub transmission valve 86, and the output of the traveling motor 39 is changed to high speed or low speed.

In addition, the swing valve 89 is provided with a swing cylinder 88 for changing the angle of the inclined plate 87 of the swing pump 41 to adjust the output, and is connected to the steering wheel 19 and the main gear lever 81 for switching. And the charge pump 78 is hydraulically connected to the swing cylinder 88 via the electromagnetic automatic steering valve 90, the steering valve 19 is used to change the swing valve 89, and the swing cylinder 88 is operated. The angle of the inclined plate 87 of the swing pump 41 is changed so that the rotational speed of the motor shaft 64 of the swing motor 42 is changed steplessly or the left and right swing operations are reversed. The pivot valve 89 is subjected to a neutral return feedback by the angle adjustment operation of the < RTI ID = 0.0 >), < / RTI > To change the left and right turning angle.

In addition, the main gear lever 81 is operated at a position other than neutral, and the steering wheel 19 is operated other than straight, so that the hydraulic output of the traveling pump 38 is proportional to the operation direction and the operation amount of the main gear lever 81. By changing the speed of the hydraulic motor 39 forward or reverse to change the forward / backward speed (vehicle speed) and changing the output of the swing pump 41 in proportion to the operation amount of the main gear lever 81, The turning radius is automatically reduced by the high speed side shifting, and the turning radius is automatically increased by the low speed side shifting, and the left and right traveling crawlers 2 are operated regardless of the traveling speed by the constant operation of the steering wheel 19. The turning radius of the circumference is kept substantially constant, and the course correction which changes the working traveling speed, the uncut straw heat, and the like and the gas is performed. On the other hand, the turning pump 41 output and the traveling pump 38 output are changed under the control of each of the 82 and 89 proportional to the operation amount of the steering wheel 19, and the turning radius (steering angle) is made smaller (larger). In this case, the driving speed of the left and right traveling crawler 2 is changed and combined by increasing the speed difference between the left and right traveling crawler 2 and turning left and right while reducing the running speed (vehicle speed) proportionally. The direction is changed by spin turn in the course correction and packing immersion, and harvesting operation is performed by mowing straw continuously and threshing. Moreover, when the main gear lever 81 is neutral, regardless of the steering wheel 19 operation, the turning valve 89 will remain neutral, and the hydraulic power output of the turning pump 41 will be kept at approximately 0, and turning The motor 42 is stopped.

14 to 22, the output shaft 44 of the engine 21 is projected on the front and rear sides, and the input shaft 45 is connected to the output shaft 44 in front of the output shaft ( The work output pulley 91 is provided on the rear side of the engine 44, and the counter case 25 is installed on the upper surface of the base 3 on the front side of the threshing unit 4 on the left side of the engine 21, and the input pulley 92 ), Vehicle speed tuning pulley 93, threshing pulley 94, mowing pulley 95, and sorting pulley 96 are supported by the counter case 25 to work the input pulley 92 behind the case 25. The belt 98 is connected to the output pulley 91 via the tension threshing clutch 97 to transmit the driving force of the engine 21 to the counter case 25. In addition, the belt 100 is connected to the vehicle speed tuning pulley 93 on the right side of the counter case 25 to the mowing drive pulley 62 of the transmission case 22 via the idle pulley 99 on the front side of the right support 24. In addition, the mowing input case 101 is rotatably supported on the support bases 23 and 24 placed on the upper surface of the base 3 in front of the base 3, and the mowing frame 12 is connected to the case 101 to connect the case ( 101. The lifting unit 7 is rotated to move up and down, and the harvesting input pulley 103 is axially supported via the harvesting input shaft 102 on the left side of the case 101, and the left side of the counter case 25 is left. The mowing pulley 95 is connected to the mowing input pulley 103 by the belt 104 to transmit driving force to each part of the mowing part 7.

In addition, the threshing pulley 94 in front of the counter case 25 is connected to the belt 106 to the drive input pulley 105 of the barrel 6, and the sorting pulley is provided at the sorting tuyere and the swinging sorting mechanism under the barrel 6. The feed chain which transmits a driving force from 96, drives each part of the threshing part 6, and installs a feed chain input shaft 107 in the left side of the said counter case 25, and is movable outside. Power is transmitted from the input shaft 107 to the drive sprocket 108 of 5). Further, a discharge drive pulley 109 is provided in front of the grain tank 15, and the pulley 109 is belt-connected to the work output pulley 91 via a discharge clutch 110 to discharge auger 17. ), The output of the engine 21 is transmitted to discharge the grains of the tank 15.

Further, the barrel input shaft 111 is axially supported on the counter case 25, the shaft 111 is extended in the front-rear direction, and threshing pulleys are provided on the front side of the shaft 111 outside the front of the counter case 25. 94), an input pulley 92 is installed behind the shaft 111 on the outside of the rear of the counter case 25, and the constant rotational power of the engine 21 is input to the barrel input shaft 111 to rotate at a constant speed. Let's do it. Further, the tuning input shaft 112 is axially supported on the right side of the counter case 25, and a vehicle speed tuning pulley 93 is provided on the right side of the shaft 112 on the right outer side of the counter case 25, and an idle pulley ( The belt 100 is tensioned between the pulleys 62 and 93 via 99 to input the vehicle speed tuning power from the transmission case 22 to the counter case 25.

As described above, the barrel input shaft 111 provided in the counter case 25 is extended in the gas front and rear direction, and the barrel input shaft 111 is penetrated in the front and rear direction of the counter case 25, and the barrel input shaft 111 is provided. The engine 21 is connected to one end side of the belt 98, and the barrel 6 is connected to the belt 106 on the other end side of the barrel input shaft 111, and the counter case 25 is a bearing of the barrel input shaft 111. It is not necessary to install an inefficient bevel gear in the barrel 6 drive system that requires a large horsepower, to improve the driving efficiency of the barrel 6 or to prevent the internal oil temperature of the counter case 25 from rising. And by changing the length of the barrel input shaft 111, the counter case 25 can be made into multiple models by easily responding to a position change in the front-rear direction of the barrel 6 or a length change in the front-rear direction of the barrel 6 and the like. To reduce the manufacturing cost, etc. in common.

In addition, a constant speed shaft 114 which is a counter shaft or a selective input shaft connecting the right side to the barrel input shaft 111 with a bevel gear 113, and a vehicle speed tuning shaft 115 installed substantially parallel to the front side of the shaft 114 are provided. , The low-speed gear 117 and the high-speed gear 118 for supporting the counter case 25 and forming the mowing speed change mechanism 116 are provided between the shafts 114 and 115, and the low-speed and neutral And a gear shifting slider 119 which performs the high speed shifting of the gears, and the gears 117 and 118 are alternatively coupled to the vehicle speed tuning shaft 115 to perform the shifting. In addition, a one-way clutch 120 for transmitting the vehicle speed tuning rotational force of the tuning input shaft 112 to the gears 117 · 118 is provided on the tuning input shaft 112, and the power from the vehicle speed tuning pulley 93 is transferred in one direction. The vehicle 120 is configured to rotate the vehicle speed coaxial shaft 115 via the gears 117 and 118 transmitted by the clutch 120.

As described above, the constant speed shaft 114, which is a counter shaft connected to the barrel input shaft 111, is provided in the counter case 25 to draw power to the side of the body, and the constant speed shaft 114 is extended to the left side of the body. The power of the sorting mechanism of the threshing part 4, the power of the feed chain 5, and the harvesting | reaping part 7 are output from the left side of the constant speed shaft 114, and simultaneously with the barrel 6 by turning on and off the threshing clutch 97 A small bevel gear 113 capable of driving or stopping the sorting mechanism to increase efficiency and durability, connects the rapid input shaft 111 to the constant speed shaft 114 of low power, and feeds the feed chain 5 or The power source of the harvesting section 7 is placed on the left side of the body, and the vehicle speed tuning shaft 115 that drives the harvesting section 7 at the vehicle speed tuning speed is installed in the counter case 25. ) Is installed approximately parallel to the constant speed shaft 114, and the fixed rotation out from the constant speed shaft 114 Simplification of the drive system of the feed chain 5 which drives the feed chain 5 by driving the feed chain 5 by the vehicle speed and the output of the vehicle speed tuning shaft 115 from the vehicle speed tuning shaft 115, and maintains a constant minimum rotation. And compaction, cost reduction, and the like, and the vehicle speed tuning shaft 115 is provided in front of the constant speed shaft 114, so that the drive system of the harvesting section 7 and the drive system of the sorting mechanism of the threshing section 4 are placed in a highly efficient layout. Install it.

In addition, the inflow gear 122 and the high speed cut gear 123 forming the mowing constant speed mechanism 121 are provided between the shafts 114 and 115, and the cutting unit 7 is driven to inflow drive or high speed cut drive. The gears 122 and 123 are alternatively coupled to the respective shafts 114 and 115 by the switching slider 124 to drive the harvesting unit 7 inflow, and the harvesting unit 7 is irrespective of the traveling state. The straw is conveyed to the feed chain 5 side, while the harvesting section 7 is driven at a high speed cut, and the harvesting section 7 is harvested by driving the harvesting section 7 at a constant rotation speed faster than the maximum speed of the vehicle speed tuning.

As described above, in the combiner which transmits power of the engine 21 to the transmission case 22 having the traveling transmission member 40 which is the traveling transmission mechanism, and drives the traveling crawler 2 which is the traveling portion, the engine 21 Power to the counter case 25 to drive the threshing part 4 by a substantially constant rotational output, and to transmit the shift output of the traveling speed shifting member 40 to the counter case 25 so that the mowing part can be driven. The counter case 25 is configured to drive (7) at a speed synchronized with the vehicle speed and to drive the harvesting section 7 at a substantially constant speed by a substantially constant rotational output of the counter case 25. By using the counter case 25 for driving the threshing unit 4 at constant speed, the harvesting unit 7 can be driven at any one of vehicle speed tuning or approximately constant speed, and part of the threshing unit 4 as a drive system is used. To drive the harvesting section 7 at constant speed. It can be configured, for mounting (7) can be achieved with such simplification and reduction of the transmission loss of the driving structure and the like.

In addition, the left end of the constant speed shaft 114 is protruded from the left side of the counter case 25 to the lower rear side, and the sorting pulley 96 is axially supported at the left end of the shaft 114. Further, the mowing motor shaft 125 is axially supported from the left side of the counter case 25 to the lower front side thereof, and the right side of the shaft 125 is connected to the vehicle speed tuning shaft 115 via the torque limiter 126, and the counter While supporting the mowing pulley at the left end of the shaft 125 projecting to the left side of the case 25, the mowing drive shaft 127 is connected to the mowing input shaft 102 to the gear 128, and the mowing drive shaft 127. ), The case 128 is rotatably installed around the longitudinal axis via the point shaft 129 on the support 23 on the left side, and the mowing input case 101 is pivotally supported. ) Is fixed to the case of the gear 128, the gear 128 is provided in each case 101, the power to be mowed from the left end side of the mowing input shaft 102 is inputted, and the case ( 101) through the mowing transmission shaft 130 to be inserted into the mowing frame 12 on the right end side. Drive the harvesting section 7 while rotating the harvesting section 7 about horizontally around the point axis 129 on the left side of the body, and maintain and repair the vicinity of each case 22 · 25 inside the body. And the like.

In addition, the input shaft 107 is chained to the feed chain drive shaft 132 which supports the feed chain input shaft 107 on the upper left side of the counter case 25 and installs the feed chain clutch 131. In addition to the connection, the feed chain transmission mechanism 134 transmits the transmission of the rotation of the constant speed shaft 114 by the change of the rotation speed of the vehicle speed tuning shaft 115, and the sun gear 135 and the planetary gear 136 are provided. And the mechanism 134 is formed by the planetary gear mechanism 138 including the ring gear 137 so as to be continuously variable, and the sun gear 135 is axially supported on the constant speed shaft 114, so that the constant speed shaft ( In addition to connecting the gear 139 to the vehicle speed coaxial shaft 115, the ring gear 137 for idling and supporting the 114 is supported, and the bearing body 140 for idling and supporting the planetary gear 136 to the constant speed shaft 114. Idling is supported, and the shaft is formed on the feed chain drive shaft 132 via the feed chain clutch 131. By connecting the receiving body 140 to the gear 141, by transmitting the rotation of the constant speed shaft 114 to the feed chain 5, while ensuring the minimum rotation required for straw conveying, by the rotation of the vehicle speed coaxial shaft 115, The feed chain 5 speed can be changed from a low constant rotation to a high rotation by synchronizing with the vehicle speed.

As described above, the counter case 25 includes a feed chain input shaft 107 that transmits a driving force to the feed chain 5, and a feed chain transmission mechanism 134 that changes the driving speed of the feed chain 5 in synchronization with the vehicle speed. And the rotation of the feed chain 5 with respect to the vehicle speed and the rotation of the harvesting section 7 to maintain a relatively constant, to ensure a good conveying water performance of the harvesting straw, and to the feed chain 5 The belt 104 of the harvesting section drive system located below the position where the power is branched is always tensioned, and the harvesting section 7 is physically constructed with a constant drive structure without installing a power cutting member such as a clutch. The structure which cannot reverse rotation makes the drive load of the harvesting | reaping part 7 become a brake in the state which made the drive input to the harvesting | reaping part 7 neutral, and the feed chain transmission mechanism by the input of the constant speed shaft 114 is made. The fixed times of the lowest from (93) To maintain the output state, thereby driven by a feed chain 5 to the predetermined rotational force of the constant-speed shaft 114.

In addition, the feed chain 5 is provided in the threshing part 4, the feed chain transmission mechanism 134 is provided in the counter case 25, and the feed chain transmission mechanism 134 is provided at the speed which synchronizes with a vehicle speed. By driving the feed chain 5, the rotation of the harvesting section 7 and the rotation of the feed chain 5 can be kept relatively constant, and the good conveying water performance of the harvesting straw can be easily ensured, and the harvesting drive structure By simplifying the operation and reducing the electric loss, the feed chain 5 is driven by the substantially constant rotational output of the counter case 25 to secure the driving speed on the low speed side, and the above-mentioned substantially constant low speed driving. It is possible to change the driving speed of the feed chain 5 in proportion to the speed of mowing operation while driving the feed chain 5 at a speed higher than the speed, while ensuring the minimum speed necessary for conveying straw. For example, mowing straw Thereby reducing the problem of clogging during the song.

In addition, the constant speed shaft 114 which is a sorting input for transmitting a driving force to the sorting mechanism of the threshing part 4, the vehicle speed coaxial shaft 115 which drives the harvesting part 7 in synchronization with a vehicle speed, and the feed chain 5 In the combiner which installs the feed chain input shaft 107 which transmits a driving force to the feed chain, the feed chain transmission mechanism 134 which changes the rotation of the constant speed shaft 114 by the rotation speed change of the vehicle speed tuning shaft 115 is provided. In the low-speed operation, the feed chain 5 is maintained at a constant level or higher so that straw can be conveyed, and the feed chain 5 is driven at high speed during the high-speed operation, and the threshing straw layer is thinned, which is necessary for threshing. In addition to reducing power, the planetary gear mechanism 138 including the sun gear 135, the planetary gear 136, and the ring gear 137 forms the feed chain transmission mechanism 134, and the constant speed shaft 114 ) And drive the sun gear 135 via the vehicle speed coaxial shaft 115 137 is rotated, the feed chain 5 driving force is transmitted to the feed chain input shaft 107 via the planetary gear 136, and the sun gear 135 is provided on the lower side of the threshing clutch 97 to supply the 6) The feed chain 5 is driven only at the time of driving, and the feed chain 5 is shifted from low constant rotation to high rotation in synchronism with the vehicle speed, and the feed chain 5 is rotated at low constant rotation during low speed operation. Drive to prevent clogging of the transfer straw. In addition, during the high speed operation, the feed chain 5 is driven at a high rotational speed synchronized with the vehicle speed, and the threshing load is prevented from being overloaded.

The hydraulic threshing cylinder 142 for operating the mowing shift slider 119, the hydraulic mowing constant speed cylinder 143 for operating the switching slider 124, and the hydraulic threshing cylinder for turning on the threshing clutch 97 ( The vehicle speed constant speed valve 147 which fixes the 144 to the flow path base 145 which is the upper cover of the said counter case 25, and operates the vehicle speed constant speed cylinder 146 which turns the constant speed clutch 76 on. And a mowing shift valve 148 for operating the mowing shift cylinder 142, a mowing constant valve 149 for operating the mowing constant cylinder 143, and a threshing valve 150 for operating the threshing cylinder 144. And a hydraulic connection to the charge pump 78 in parallel.

Moreover, as shown in FIG. 15, FIG. 23-FIG. 28, the threshing clutch 97 is axially supported by the tension arm 151, and the support shaft 152 of the counter case 25 is carried out. The tension arm 151 is rotatably axially supported, and the piston rod 155 of the threshing cylinder 144 is connected to the tension arm 151 through two bendable links 153 and 154, and the piston rod ( The threshing clutch 97 is turned on by the pressing (entering) operation of the 155 to tension the belt 98 while the threshing clutch 97 is turned off by the pulling (retraction) operation of the piston rod 155. The belt 98 is loosened by operating. In addition, the spring 156 for suppressing the threshing clutch 97 on the off side is connected to the link 154, and on the return side of the flow path on the piston rod 155 advance side of the double acting threshing cylinder 144. The throttle valve 157 is installed, the piston rod 155 is advanced at a slow speed to turn on the threshing clutch 97, while the piston rod 155 is retracted at a high speed to turn the threshing clutch 97 off. do.

As is clear from the above, the counter case 25 which is an electric case which distributes the power from the engine 21 to the traveling crawler 2 which is a traveling part, the threshing part 4 which is a working part, and the harvesting | reaping part 7 is provided. In the work vehicle described above, a threshing clutch 97 serving as a work clutch or a plurality of hydraulic cylinders 142. 143. 144 for work shifting is provided on the flow path base 145 forming a part of the counter case 25. The hydraulic cylinders 142, 143, and 144 can be used for switching both the inside and the outside of the counter case 25, thereby making the hydraulic switching structure compact, improving maintenance and repair, and the like. The pistons 160 and 161 of the hydraulic cylinders 142 and 143 for shifting are incorporated in the counter case 25 so that the piston rod 155 of the hydraulic cylinder 144 for the threshing clutch 97 is mounted in the counter case 25. Inside and outside the counter case 25 by The switching structure such as shifting or clutch can be compactly arranged around the flow path base 145 which is a part of the counter case 25, and the support rigidity of the hydraulic cylinders 142, 143 and 144 for the switching reaction is flow path-based. By attaching 145, it can be ensured easily and the adhesion removal property, maintenance, repairability, etc. can be improved.

In addition, by connecting the piston rod 155 of the hydraulic cylinder 144 for the threshing clutch 97 to the tension arm 151 of the belt clutch forming the threshing clutch 97, the capacity of the hydraulic cylinder 144 is increased. By increasing the tension, the tension force required for the belt clutch can be sufficiently obtained, compactness and improvement of maintenance and repairability are performed, and the hydraulic cylinder 144 for the threshing clutch 97 is double acting to turn the belt clutch on and off. By hydraulically operating both of them, by increasing the capacity of the hydraulic cylinder 144, the tension force required for the belt clutch can be sufficiently obtained, thereby making it compact and improving maintenance and repairability. Moreover, by driving the hydraulic cylinder 144 for threshing clutch 97 using the hydraulic charge pump 78, the hydraulic force of the charge pump 78, the diameter of the piston 155 of the hydraulic cylinder 144, The tension force can be easily determined by the ratio of the tension arm 151, and no tension adjustment is required, thereby improving maintenance and repairability, and hydraulic pressure cylinder for the threshing clutch 97 rather than the maximum extension amount of the belt 98. By increasing the lock of the piston rod 155 of 144, even if the belt 98 is extended, it is possible to easily secure an appropriate tension without adjusting the tension.

As shown in FIGS. 15 and 27 to 32, the upper surface of the counter case 25 is fastened with a bolt 158 to be detachably fastened so that the counter case 25 can be fixed. While closing the upper surface opening 159, the respective valves 148, 149, 150 are fixed to the upper surface side of the flow path base 145, and the cylinders 142. 143 占 144 is fixed, threshing cylinder 144 is provided in the outer side of the counter case 25, and the mowing transmission cylinder 142 and the mowing constant cylinder 143 are provided in the counter case 25 inside. Further, arm rods 162 占 163 protruding the piston rods 160 占 161 from opposite sides facing the cylinders 142 占 143 in opposite directions, and forming a rear cover of each cylinder 142 占 143. The shafts 166 and 167 on one end of the transmission arm 164 and the constant speed arm 165 are rotatably inserted from below to support the shaft, and the respective pistons on the other end of the arms 164 and 165. The rods 160 and 161 are connected.

In addition, the fork shaft 168 is rotatably installed at the periphery of the shaft in substantially parallel to the vehicle speed tuning shaft 115 in the counter case 25, and the shift fork 169 for switching the mowing shift slider 119, And a fixed speed fork 170 for switching the switching slider 124 on the fork shaft 168 so as to be slidable in the axial center direction, and each pin 171... 172 is coupled to each of the forks 169 and 170, and each arm 164 and 165 is connected to each of the forks 169 and 170, and the respective cylinders 142 and 143 are controlled by the respective valves 148 and 149. The piston rods 160 · 161 of the head) to advance or retract, and swing the arms 164 占 165 around the point shafts 166 占 167, thereby shifting the transmission fork 169 from neutral to high speed or standard (low speed). While moving to the output side, the constant speed fork 170 is configured to move from neutral to the high speed cut or inlet rotation output side have.

As mentioned above, in the combine which installs the traveling transmission member 40 which is the hydraulic traveling transmission mechanism which transmits the power of the engine 21 to the transmission case 22, it synchronizes with a vehicle speed via the traveling transmission member 40, for example. A vehicle speed tuning shaft 115 for driving the mounting 7 and a constant speed shaft 114 for directly transmitting the driving force of the engine 21 are provided, and any one of the vehicle speed tuning shaft 115 and the constant speed shaft 114 is provided. Is selected to drive the harvesting section 7. When the mowing operation is at the highest speed, the vehicle shifts from the vehicle speed tuning rotation to the constant rotation, and the volumetric efficiency of the hydraulic transmission pump 38 and the motor 39 of the traveling transmission member 40 becomes approximately the highest (100 percent). When the harvesting section 7 is driven by the constant speed shaft 114 in the constant rotation, the rotation speed during the constant rotation becomes higher than the rotation of the vehicle speed tuning, and the traveling transmission member 40 is driven to drive the harvesting section 7. Since the harvesting section 7 is driven by an efficient mechanical drive system, the engine 21 power can be utilized for driving the threshing section 4 by the power loss of the traveling transmission member 40. The work efficiency can be improved, and the fuel efficiency of the engine 21 can be improved.

14, 29, and 30, the back pressure rod 174 is fixed to the piston rods 160 and 161 via the piston head 173, and the outer circumference of the back pressure rod 174 is also fixed. A ring-shaped retracting piston 175 is provided in the upper portion, a back pressure rod 174 is formed at a smaller diameter than the piston head 173 at a larger diameter than the piston rods 160 and 161, and the outer diameter of the retracting piston 175 is defined as a piston head ( When the valves 148 and 149 are neutral and the valves 148 and 149 are neutral, the inlet piston 175 is pushed by the A port 176 of the charge pump 78 to the step 177 of the cylinders 142 and 143. ), The piston head 173 is brought into contact with the retraction piston 175 by the B port 178 pressure oil of the charge pump 78, and the piston rods 160, 161 are moved to the neutral position by the hydraulic force. Support by double acting. When the valves 148 and 149 are switched, the B port 178 is opened in the tank passage of the valves 148 and 149, so that the back pressure rod 174 and the head (B) are pressurized by the A port 176 pressure oil. 173 and the piston rods 160 and 161 advance, while opening the port A 176 to the tank passage of the valves 148 and 149, whereby the head 173 and the back pressure rod are formed by the B port 178 pressure oil. 174 and the retraction piston 175 and the piston rod 160 · 161 retreat, and the arm 164 · 165 doubles and is fixed to the neutral position via the piston rod 160 · 161 in a pressurized state. The sliders 119 and 124 can be returned to the neutral position and supported without installing a spring or the like. In addition, a lubrication port 179 is formed in the step 177 of the cylinders 142 and 143 to communicate the port 179 with the A port 176 or the B port 178.

As evident from the above, the piston rods 160 · 161 and the retracting piston 175 of the double-acting hydraulic mowing shifting and mowing constant speed cylinders 142 · 143 are doubled to be supported in neutral by applying pressure to both sides. By the neutral operation of the three-position switching valves 148 and 149, the piston rods 160 and 161 and the retraction piston 175 can be held in a neutral position by hydraulic pressure, and the cylinder 142 and 143 may be in one direction of the main body. The double-acting cylinders 142 占 l43 protruding the piston rods 160 占 161 can make the three-position switching appropriately, and a compact and reliable switching mechanism can be constituted. Alternatively, the switching mechanism in one direction or in both directions of the constant speed mechanism 121 may be simplified and the operability may be improved.

Moreover, as shown in FIG. 32, while supporting the said fork 169 * 170 at the neutral position by the detent ball 180, it is a right angle (vertical angle) in the direction orthogonal to the axial center direction of the fork shaft 168. And a square hole shift cam (181) to the boss portion of the shift fork 169 and insert the pin 182 through the fork shaft 168 and the shift cam 181. In addition, a long hole-shaped constant speed cam 183, which is inclined with respect to the fork shaft 168, is installed on the boss portion of the constant speed fork 170, and the pin 184 is attached to the fork shaft 168 and the constant speed cam 183. Insert through. Then, by switching the speed change fork 169 to the mowing standard (low speed) or the high speed side, the pin 182 contacts the right angle portion of the speed change cam 181 in the axial center direction of the fork shaft 168, and the fork shaft 168 It prevents the rotation around the shaft center of and supports the constant speed fork 170 in a neutral position. On the other hand, by switching the constant speed fork 170 to the high speed cut or the input rotation side, the pin 184 is pushed by the constant speed cam 180 to rotate the fork shaft 168 around the shaft center, and the shaft center of the fork shaft 168 The pin 182 is contacted with the right angle part of the transmission cam 181 of orthogonal direction, the movement of the transmission fork 169 is prevented in the axial direction, and the transmission fork 169 is supported in a neutral position. Thus, the transmission fork 169 and the constant speed fork 170 are provided on one fork shaft 168, and the operation | movement of each fork 169 * 170 is mutually operated by the transmission cam 181 and the constant speed cam 183. By regulating and simultaneously switching, the occurrence of meshing of the gears 117, 118, 122, and 123 is prevented.

As apparent from the above, in the combiner including a mowing transmission mechanism 116 for changing the drive speed of the mowing section 7 and a mowing constant speed mechanism 121 for driving the mowing section 7 at substantially constant speed, It is possible to switch the mowing transmission mechanism 116 when the mowing constant speed mechanism 121 is neutral, and the output of the other rotational speeds of the above mechanisms 116 · 121 is simultaneously transmitted to the mowing part 7. Can be eliminated, the constant speed output of the mowing constant speed mechanism 121 is prioritized to the output of the mowing transmission mechanism 116 and transmitted to the mowing part 7, whereby the mowing part 7 can be smoothly driven, It is possible to reduce the occurrence of the drive trouble of (7), improve the driving operability, and operate the constant speed fork 170, which is the forward rotation operation tool of the mowing constant speed mechanism 121, other than neutral, thereby making the mowing transmission mechanism ( By making 116 neutral, the mowing constant speed mechanism 121 exits other than neutral. When switching to the force, trouble such as returning the mowing mechanism 116 to neutral or confirming that it is neutral, can be reduced, and driving operability is improved.

In addition, the transmission fork 169 which is a shift operation tool for switching the mowing transmission mechanism 116 and the constant speed fork 170 for switching the constant speed mechanism 121 are provided on the fork shaft 168 which is the same operation shaft. In addition, by installing a shifting cam 181 and a constant speed cam 183, which are regulating mechanisms that check the switching operation of the forks 169 and 170, the fork shafts 168 are shared, and the forks described above are shared. Since 169 * 170 is provided, each fork 169 * 170 can be assembled and adjusted easily, and each fork 169 * 170 can be easily connected by the cam 181 * 183. It is possible to simplify the shift operation structure, reduce the size of the shift operation structure, and improve the shifting operability. The cam shaft 168 to which the shifting and forward rotation forks 169 and 170 are rotatably installed and the fork shaft 168 is provided. The pins 182 and 184 of the pins 182 and 184 into the through holes of the forks 169 and 170 to form the cams 181 and 183. 168 can be used effectively, and the cams 181 and 183 can be provided, and the pins 182 and 184 and the through-holes make the cams 181 and 183 simple and highly functional. It aims to simplify the structure and make it compact and to improve the shift operability.

Moreover, as shown in FIG. 17, 20-22, the fastening seat 185 formed in the said counter case 25 is fastened and fastened to the base 3, and the counter case is fastened. The detaching case 187 is detachably fastened to the outer side of the 25 so that the bolt 188 is fastened and detached, and a part of the counter case 25 is formed by the separating case 187, and the detaching case 187 is detached. By forming the outer side surface of the counter case 25 so that opening and closing is possible, the said shaft 107 * 114 * 115 * 125 * 132 is axially supported by the counter case 25 and the separation case 187, and a counter Compared to the case 25 upper surface opening 159, when the separation case 187 is removed, the opening area of the outer side of the case 25 is increased, and the respective shafts 107, 114, 115, 125, 132 are detached and It is comprised so that gear replacement etc. can be performed.

As apparent from the above, the work vehicle includes a counter case 25 for distributing the power from the engine 21 to the traveling crawler 2 serving as the traveling portion, the threshing portion 4 serving as the working portion, and the harvesting portion 7. In the above, the opening 159 that can be opened and closed on the upper surface of the counter case 25 is opened, and the opening 159 is opened to hold the inside of the counter case 25 through the opening 159. The separation case 187 which forms a part of the counter case 25 can be repaired and handleability can be improved, and as a cover of the outer side part of the counter case 25 so that removal is possible, In the case where the separation case 187 is removed, the opening area of the outer side portion of the counter case 25 is formed larger than the opening 159 on the upper surface, and the counter case 25 is removed by removing the separation case 187. Replace gears or shafts inside In addition, damage can be checked and maintenance and repairability can be improved.

In addition, the opening 159 of the upper surface of the counter case 25 is closed to be opened and closed by the flow path base 145 equipped with the hydraulic cylinders 142 占 l43 占 144 and the hydraulic valves 148 占 149 占 150. Since the hydraulic components are unitized so that the cover of the counter case 25 can be used as a unit, the structure can be made compact and the maintenance and repairability can be improved, and the support members 23 and 24 of the harvesting section 7 are provided. ) And the separate case 187 are separately configured, and the counter case 25 is fixed to the machine to fix the separate case 187 to the counter case 25. ) Can be easily attached or removed, and the handleability of maintenance and repair can be improved.

33, the threshing switch 190 which detects the threshing operation of the work lever 189, the mowing switch 191 which detects the mowing operation of the work lever 189, and the mowing shift slider ( Cutting gear switch 192 for switching between low speed and high speed of 119, high speed operation switch 193 and reverse switch 194 for detecting switching of the high speed forward and reverse of the peripheral speed lever 81, and the operator's The manual inflow switch 196 which detects the stepping-down of the inflow pedal 195 and the sub transmission switch 197 which performs low speed and high speed sub-shift switching are connected to the job controller 198 comprised with a microcomputer.

In addition, the direct drive switch 199 for manually switching to the operation of driving the harvesting section 7 by a constant rotational output of the engine 21, and the automatic switch 200 for turning on and off the manual input of the switch 199. ), Left and right vehicle speed sensors 201 and 202 for detecting the speed (vehicle speed) of the left and right traveling crawler 2, straw sensors 203 for detecting the presence or absence of conveying straw of the harvesting section 7, The cutting input sensor 204 for detecting the input rotational speed of the tuning input shaft 112 for inputting the driving force of the vehicle speed tuning to the cutting unit 7 via the low speed gear 117, and the cutting gear cylinder 142 at a low speed or The cutting low speed and cutting high speed solenoids 205 and 206 for switching at high speed, the feed chain solenoid 191 for operating the feed chain clutch cylinder to turn off the feed chain clutch 131, and the constant rotation cylinder 143 Inlet solenoid 20 for coupling the switching slider 124 to the inlet gear 122. 8) and the high speed cut solenoid 209 which couples and operates the switching slider 124 to the high speed cut gear 123 by the constant speed cylinder 143 to the job controller 198, and the flow chart of FIG. Similarly, the harvesting section 7 is operated at the inflow speed, the high speed cut speed, or the vehicle speed tuning speed.

The harvesting section which drives the feed chain 5 at a speed synchronized with the vehicle speed while ensuring a constant minimum speed, and is detected by the harvesting input sensor 204 under the condition that the conveying straw is present in the harvesting section 7. When the driving speed of (7) is slowed down, the inflow solenoid 208 is operated to automatically perform the operation of driving the harvesting section 7 at the input speed, for example, to the inflow pedal 195 as in the prior art. Compared to the inflow operation of the harvesting section 7 only by manual operation by the manual operation, the problem of forgetting the inflow operation or the timing shift is eliminated, and the straw is prevented from clogging.

Further, when the high speed drive switch 193 is turned on when the automatic switch 200 is in the on state, the high speed drive solenoid 211 for turning on the constant speed clutch 76 and the subshift switch 197 described above. The threshing clutch is operated by turning on the threshing switch 190 and the sub-low speed and high speed solenoids 212 · 213 for operating the sub-shift cylinder 85 by switching to make the traveling motor 39 low speed or high speed output. The threshing clutch solenoid 214 which turns 97 on is connected to the job controller 198.

As shown in the flow chart of FIG. 34, when the threshing switch 190 is turned on by the operation of the work lever 189, the feed chain solenoid 207 is turned on and the feed chain clutch 131 is turned on. Then, the drive of the feed chain 5 is started, the threshing clutch solenoid 214 is operated to turn on the threshing clutch 97, and the threshing part 4 and the feed chain 5 are driven.

In addition, when the harvesting switch 191 is turned on by the operation of the work lever 189, the peripheral speed driving force is transmitted to the harvesting unit 7 via the vehicle speed tuning pulley 93. At this time, when the inflow pedal 195 is pressed and the inflow switch 196 is turned on, the input rotational speed of the vehicle speed tuning of the harvesting unit 7 detected by the harvesting input sensor 204 is applied to the inflow gear 122. When the rotational speed is lower than the rotational setting, the shifting shift slider 119 is moved to the neutral position to turn the shift speed output of the shifting mechanism 116 into neutral to turn off the transmission of the vehicle speed tuning input shaft 122, and further, the inflow solenoid 208. ) Is driven to drive the harvesting section 7 at a lower speed than the high speed cut gear 123 via the input gear 122. On the other hand, when the inflow switch 196 is turned on, if the input rotation speed of the vehicle speed tuning of the harvesting section 7 is equal to or greater than the rotation setting by the inflow gear 122, the harvesting shift output of the harvesting transmission mechanism 116 is neutralized. By turning off the transmission of the tuning input shaft 112 and by the operation of the high speed cut solenoid 209, the cutting unit 7 is driven at the highest rotation speed higher than the inlet gear 122 via the high speed cut gear 123. Drive at constant speed.

In addition, when the reverse switch 194 is off, when the axle 55 detected by the vehicle speed sensors 201 and 202 is stopped, the vehicle speed of the harvesting unit 7 is made neutral by making the mowing speed change mechanism 116 neutral. Stop tuning operation. On the other hand, if the axle 55 is driven, the input rotation of the vehicle speed tuning of the harvesting | reaping part 7 detected by the harvesting input sensor 204 will be a high speed cut gear when the sub-shift output of the travel motor 39 is low speed. When the rotation setting by 123 is abnormal, the high speed cut solenoid 209 is operated to make the mowing transmission mechanism 116 neutral, and the mowing part 7 is driven at constant speed via the high speed cut gear 123 at the highest speed. A high speed cut operation is performed.

When the sub-shift output of the traveling motor 39 is at low speed, when the input rotation of the harvesting unit 7 is at or above the setting, and the direct drive switch 199 is turned on when the automatic switch 200 is on, high-speed operation By operating the solenoid 211 to turn on the constant speed clutch 76 and directly transmit the driving force of the engine 21 from the constant speed clutch 76 to the sub transmission mechanism 47 without intervening the travel transmission member 40. To operate the high-speed drive.

Further, when the direct drive switch 199 is off, by operating the mowing shift switch 197, the mowing shift output of the mowing shift mechanism 116 is switched to low speed or high speed, and the respective gears 117 · 118 The harvesting section 7 is driven at low speed or high speed by the vehicle speed tuning input through one direction, and the standing straw is harvested at a low speed or the straw being covered at high speed.

In addition, as shown in the flow chart of FIG. 35, when the key switch for operating the engine 21 is turned on and power is supplied to the job controller 198, the low-speed solenoid 212 is turned on and the sub-shift valve ( 86 is operated to switch the inclined plate 84 of the travel motor 39 at low speed. Then, by changing the angle of the inclined plate 79 of the travel pump 38 by the main gear lever 81, the sub-shift valve 86 is operated at high speed by driving the sub-shift switch 197 at a high speed. In addition to switching, when the sub transmission switch 197 is operated at a low speed and the sub transmission valve 86 is switched at a low speed, the traveling pump 38 is operated so that the traveling pump 38 is at the highest speed. In the vicinity of the maximum speed at which the volumetric efficiency of (38) becomes 90 to 95 percent, the high speed operation switch 193 is turned on by the main speed lever 81, and the maximum speed operation of the main speed lever 81 is detected. , The low speed and high speed solenoids 212 · 213 are automatically turned off to keep the sub transmission valve 86 neutral, and the sub transmission cylinder 85 is shorted to the oil tank side to free the piston of the cylinder 85. The discharge hydraulic pressure of the traveling pump 38 flows in and out of the charge pump 78. To this end, the inclination plate 84 of the travel motor 39 is returned to the neutral side by the pump 38 hydraulic pressure, the high speed driving solenoid 211 is automatically turned on, and the vehicle speed constant speed valve 147 is switched. The constant speed clutch 76 is turned on by operating the vehicle speed constant speed cylinder 146, and the driving force of the engine 21 is transmitted from the constant speed clutch 76 to the sub transmission mechanism 47 without the travel transmission member 40 interposed therebetween. Is transmitted directly to drive the crawler 2 on either side. Moreover, after switching the valve 147 by making the piston of the cylinder 85 free, the cylinder 85 may be fixed to the low speed side or may be free. After the constant speed clutch 76 is turned on, approximately 0.2 seconds have elapsed, the sub transmission valve 86 is neutral, and the inclined plate 84 of the traveling motor 39 is delayed to be free.

36 shows the relationship between the angle of the inclined plate 79 of the traveling pump 38 and the hydraulic endless output speed, and when the volume efficiency at which the inclined plate 79 of the traveling pump 38 is inclined at maximum is 100 percent. With respect to the maximum speed calculated value, the lost horsepower (5 to 10 percent) at the maximum angle of the inclined plate 79 is subtracted, so that the actual speed output actually outputs the low speed, but the pump shaft is provided via the constant speed clutch 76. The gear transmission ratio for gear 73 and the motor shaft 46 is set such that the volumetric efficiency of the traveling pump 38 is approximately equal to the speed at the maximum speed calculated value of 100 percent and the speed at the output side of the motor shaft 46. As a result, the traveling crawler 2 is driven at the speed of the maximum speed calculated value via the constant speed clutch 76. In addition, when the pump shaft 73 and the motor shaft 46 are directly connected via the constant speed clutch 76, the sub transmission valve 86 becomes neutral, and the angle of the inclined plate 84 of the travel motor 39 becomes hydraulic. It changes freely by this, keeps the rotational load of the motor shaft 46 smallest, and collects the hydraulic loss horsepower of the traveling transmission member 40 effectively.

As apparent from the above, in a work vehicle including a traveling transmission member 40 that is a hydraulic traveling transmission mechanism that changes the driving speed and a constant speed clutch 76 that is a constant speed mechanism that drives at approximately constant speed, the traveling transmission member 40 The output variable structure of the hydraulic drive motor 39 of () is fixed, and the output variable of the hydraulic drive motor 39 is fixed to the low speed side before the direct drive operation of the constant speed clutch 76 is performed. As described above, the traveling crawler 2 is driven by the speed change outputs of the hydraulic traveling pump 38 and the traveling motor 39 of the traveling transmission member 40 at a speed of less than or equal to the maximum speed, The output side of the traveling transmission member 40 is connected by the constant speed clutch 76, and the hydraulic traveling motor 39 of the traveling transmission member 40 is configured as an output variable structure, and the connection of the constant speed clutch 76 is an example. For example, by fixing the output variable of the hydraulic traveling motor 39 to the constant speed at about the same, the variable speed output of the hydraulic traveling motor 39 can be varied so that the speed change range of the traveling transmission member 40 can be expanded. However, there is a problem that the output of the traveling transmission member 40 tends to be unstable. Therefore, when the drive of the traveling crawler 2 and the harvesting section 7 is started by the output of the traveling transmission member 40, the output of the hydraulic traveling motor 39 is locked substantially constant, so that the hydraulic traveling pump ( By varying the output of only 38, the drive of the traveling crawler 2 and the harvesting section 7 can be started by the stable output of the traveling transmission member 40, improving the driving operability and handling, and the constant speed clutch. When the output variable of the hydraulic traveling motor 39 is made free by the output operation of 76, when the input side of the hydraulic traveling pump 38 and the output side of the hydraulic traveling motor 39 are directly connected, the hydraulic traveling motor 39 By freeing the output adjustment of), the hydraulic driving motor 39 is output adjusted by the hydraulic load of the motor 39 so that the main circuit hydraulic pressure becomes the lowest according to the discharge amount on the hydraulic driving pump 38 side, and the hydraulic traveling pump Each discharge amount of the 38 and the traveling motor 39 can be easily worked. May be, it is possible to state the hydraulic pressure of the hydraulic circuit decreases smoothly with primary pressure, it is possible to effectively recover the loss of horsepower of the hydraulic transmission device, the reduction of kkoehanda simplified and the electric losses of the drive structure.

Moreover, the drive transmission member 40 which is a hydraulic transmission mechanism which converts the power of the engine 21 into the hydraulic continuously variable speed output and drives the traveling crawler 2 which is a traveling part, and the input side and the output side of the said traveling transmission member 40 are connected directly. In the work vehicle provided with the constant speed clutch 76 which is a constant speed mechanism which is supposed to make WHEREIN, the transmission ratio of the said constant speed clutch 76 side is set so that it may become the maximum speed calculation value of the traveling transmission member 40. FIG. Then, by setting the gear transmission ratio on the constant speed clutch 76 side so that the volumetric efficiency of the traveling speed shifting member 40 is approximately equal to the output of about 100 percent (to increase several percent), for example, the traveling speed shifting member 40 ), When the volumetric efficiency is 90 to 95 percent or more, the output becomes unstable, and an output loss of 5 to 10 percent occurs and the oil temperature rises, even if the traveling transmission member 40 is near the highest speed (for example, volumetric efficiency). When the speed is increased to 90 to 95 percent), the constant speed clutch 76 is directly connected, the output loss when operating at the maximum speed is reduced, and the loss horsepower of the hydraulic transmission is speeded up near the maximum speed. By smoothly shifting the speed of the maximum speed calculated value, it is possible to provide a stable top speed in an inexpensive structure and to improve driving performance.

In addition, the traveling variable member 40 is provided with the hydraulic traveling pump 38 of the output variable structure and the hydraulic traveling motor 39 of the output variable structure, and the output variable of the hydraulic traveling motor 39 is made free. Thereafter, the constant speed clutch 76 may be directly connected to each other, and the shock caused by the speed difference when switching from the output of the traveling transmission member 40 to the output of the constant speed clutch 76 is reduced, and the constant speed clutch ( Under the state of outputting through 76), the operating oil pressure of the hydraulic traveling motor 39 is lowered to the charge pump 78 oil pressure, thereby reducing the driving load of the traveling transmission member 40 in the idle state. The driving performance is improved at the highest speed by the constant speed clutch 76.

9 and 12, although the constant speed clutch 76 was provided on the pump shaft 73 of the traveling pump 38, on the constant speed shaft 77 instead of the pump shaft 73. In addition to the constant speed clutch 76, the constant speed cylinder 146 incorporated in the constant speed clutch 76 by disposing the vehicle speed constant speed valve 147 on one side of the pump shaft 73, which is the lockup constant speed shaft, is described above. The hydraulic piping between the valves 147 is unnecessary. It is also possible to incorporate a gear for multistage transmission into the gear connecting portion of the constant speed clutch 76 and to switch the lockup speed of the constant speed clutch 76 to multiple stages.

37 and 38 show the deformable structure shown in Fig. 16, and the ball clutch type constant speed clutch 215 which detachably couples the low speed and high speed gears 117 · 118 to the tuning input shaft 112. Figs. On the tuning input shaft 112, and transmits the power from the vehicle speed tuning pulley 93 to the vehicle speed tuning shaft 115 by the one-way clutch 120, via the gear 117 占 118. The tuning input shaft 112 and the vehicle speed tuning shaft 115 are configured to rotate in conjunction with the constant speed clutch 215. In addition, the high speed drive solenoid 217 for operating the constant speed drive cylinder 216 on the constant speed clutch 215 is connected to the job controller 198, and the cutting unit 7 is connected to an input speed, a high speed cut speed, or a vehicle speed. In addition to operating at a tuning speed, a constant rotational force is transmitted from the counter case 25 to the output side of the hydraulic driving motor 39 of the traveling transmission member 40, which is a hydraulic traveling transmission mechanism, and is shifted at a higher rotation than the output of the motor 39. The traveling crawler 2 is directly driven without passing through the member 40.

As mentioned above, in the combine which installs the traveling transmission member 40 which is the hydraulic traveling transmission mechanism which transmits the power of the engine 21 to the transmission case 22, the engine 21 power is transmitted to the threshing part 4. As shown in FIG. The fixed speed shaft 114 is provided below the threshing clutch 97 to transmit the power of the constant speed shaft 114 to the output side of the traveling transmission member 40 and the constant speed clutch 215. Install it. Then, for example, the engine 21 output is transmitted to the output side of the traveling transmission member 40 through the constant speed clutch 215 at the highest speed of operation, so that the hydraulic pressure of the traveling transmission member 40 is taken as the charge pressure. The shift loss is eliminated, the power loss of the driving drive by the traveling transmission member 40 is reduced, the fuel economy of the engine 21 is improved, and the oil cooler of the traveling transmission member 40 is formed in a small capacity. For example, even if the running load such as the change of direction in a wet field increases, the operator performs driving operation without feeling the running force shortage, to reduce the output loss of the engine 21, etc. By recovering the power loss, the traveling crawler 2 is driven at the highest speed with high efficiency, enabling the highest speed work with a sufficient driving force to improve driving operability.

In addition, when the work vehicle speed transmitted through the travel transmission member 40 is near the highest speed, the constant speed clutch 215 is turned on manually or automatically, and the work speed is the highest speed by turning on the constant speed clutch 215. And the power loss caused by the traveling transmission member 40 in the vicinity of the highest speed is compensated for by the input rotation from the constant speed clutch 215, and since the power required for the increase in the vehicle speed is small, the remaining engine 21 power Is used to drive the work unit, secures the power necessary for the highest speed operation, and drives the driving force at a rotational speed approximately equal to the rotational speed at which the volume shifting efficiency of the traveling speed shifting member 40 becomes almost 100 percent. ) Is transmitted to the power transmission system of the driving part such as the traveling crawler 2, and the engine 21 power is designed in accordance with the highest work speed, so that the power can be afforded up to the vicinity of the highest speed, With the free been eliminated, it is possible to expect the same effect as when sikyeoteul increase the engine 21 horsepower by the number of power losses, thereby easily ensuring the necessary power for the fastest operation. For example, the vehicle speed (for example, 5 percent) may be accelerated by the difference in the volumetric efficiency of the traveling transmission member 40. (I.e., if the volumetric efficiency of the hydraulic transmission mechanism 107 at the highest work speed is about 95 percent, the input rotational speed from the constant rotation clutch 78 is set to an output rotational speed of 100 percent volumetric efficiency. By this, since the driving speed of the constant speed clutch 215 is forcibly driven so that the output rotation speed becomes 100 percent of the volumetric efficiency, the vehicle speed is increased by 100 percent to 95 percent = 5 percent by this minute. Therefore, the power required for the speed increase of the vehicle speed is small, and the remaining engine 21 power is used for driving the work part, thereby securing the power required for the highest speed work.

As described above, when the transmission output of the traveling transmission member 40 is near the highest speed, the vehicle travels from the substantially constant rotational output constant speed clutch 76 or 215 which is about the same as when the transmission efficiency of the traveling transmission member 40 is the highest. By conveying to the output side of the transmission member 40, even if the power transmission efficiency of the traveling transmission member 40 decreases due to the increase in the traveling load near the highest speed, the drive speed of the traveling crawler 2 is prevented from decreasing. The driving speed of (7) can be maintained appropriately, the high speed operation of increasing load can be performed stably, for example, problems such as clogging of cutting straws can be reduced, and the driving structure can be simplified. And reduction of transmission loss.

In addition, when the work vehicle speed falls near the work maximum speed, the constant speed clutch 215 is automatically turned off, for example, even if the operator deliberately performs an operation of lowering the work vehicle speed from the work maximum speed vicinity, the constant speed clutch 215 By turning off) automatically, the engine 21 power is designed to work at the highest speed, so that the power can be reduced to the vicinity of the highest speed. Even if the operator does not recognize that the working vehicle speed has fallen from the maximum working speed, the highest speed working state is automatically released by lowering the working vehicle speed, thereby improving durability of the engine 21 and improving fuel economy.

Claims (6)

In the combiner which transmits power of an engine to a transmission case provided with a traveling transmission mechanism, and drives a drive part, the engine power is transmitted to a counter case, and a threshing part is driven by a substantially constant rotational output, The combine case is configured to transmit the shift output to the counter case to drive the harvesting section at a speed synchronized with the vehicle speed, and to drive the harvesting section at about constant speed by the substantially constant rotational output of the counter case. . The combine according to claim 1, wherein when the transmission output of the traveling transmission mechanism is near the highest speed, a constant rotational output is approximately transmitted to the output side of the traveling transmission mechanism, which is about the same as when the transmission efficiency of the traveling transmission mechanism is the highest. 2. The speed changing output of the traveling speed transmission mechanism and the hydraulic traveling pump of the traveling speed transmission mechanism drives the traveling portion, and the output side of the traveling speed transmission mechanism is connected by the constant speed mechanism near the highest speed. And the output variable structure of the hydraulic traveling motor is fixed before connecting the constant speed mechanism to the hydraulic traveling motor of the traveling transmission mechanism. The combine of Claim 5 which makes the output variable of a hydraulic traveling motor free by the output operation of a constant speed mechanism. The combine chain according to claim 1, characterized in that the feed chain includes a feed chain, a feed chain transmission mechanism is provided in the counter case, and the feed chain is driven at a speed synchronized with the vehicle speed through the feed chain transmission mechanism. The method according to claim 5, wherein the feed chain is driven by a substantially constant rotational output of the counter case to secure the driving speed on the low speed side, and the feed chain is synchronized with the vehicle speed on the high speed side than the above-mentioned substantially constant low speed driving speed. Combines characterized by driving at speed.