JP3801543B2 - Combined transmission structure - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a power transmission structure for a combine configured to travel with left and right crawler travel devices.
[0002]
[Prior art]
In a combine, a hydraulic continuously variable transmission (HST) excellent in operability is often used as a main transmission for traveling. For example, as disclosed in JP-A-2002-104229, an engine is used. The continuously variable transmission driven by the gear is connected to the traveling transmission case, the shift output from the continuously variable transmission is branched into the traveling system and the working system in the transmission case, and the power of the branched traveling system is The sub-transmission mechanism is shifted to a plurality of stages and then distributed and transmitted to the left and right crawler travel devices, and the power of the branched work system is transmitted to the mowing work section via the PTO shaft provided in the transmission case. Are known.
[0003]
[Problems to be solved by the invention]
According to the configuration in which the traveling system and the working system are driven by a common continuously variable transmission, the mowing operation unit can be driven at a speed synchronized with the traveling speed, so that the posture of raising the grain at the time of mowing is stabilized. Although it has an advantage, if the work is performed while traveling at a low speed, the driving speed of the mowing unit will be slowed accordingly, the cutting blade speed of the mowing device will be slowed, and the mowing performance will be lowered or raised. The apparatus is prone to problems such as the apparatus being pulled up and the claw moving speed slowed down and the cereals are pulled out. In addition, when driving at the maximum speed, the driving speed of the mowing work section is increased accordingly, the wear at various operating parts of the mowing work section is likely to progress, and driving noise is likely to be generated, etc. The problem was likely to occur.
[0004]
In addition, in a single field, the level of crop lodging is rarely uniform, and in many cases, it is partially raised or in a lying state. In the combine of the above transmission structure, The following gear shifting operations are performed according to the conditions of the crop. For example, if the crop is locally lying in the napped state, the sub-transmission mechanism of the traveling system is selected as the standard gear stage in the napped region and synchronized with the traveling speed. Raise and mow crops at standard speed. In addition, when the local lodging area is reached, the sub-transmission mechanism of the traveling system is switched to a low speed stage to relatively increase the driving speed of the mowing operation section with respect to the traveling speed, and the crop is reduced at a sufficient speed while traveling slowly. Cause and reap. Then, when the harvesting in the lodging region is over and the napped region is entered, the auxiliary transmission mechanism is again switched to the high speed stage to return to the standard harvesting state.
[0005]
Therefore, it is necessary to frequently adjust the traveling speed and switch the auxiliary transmission mechanism in a field where napping and lodging are complicated and mixed, and the operation is troublesome and requires skill.
[0006]
The present invention has been made paying attention to such points, and an object thereof is to enable easy and easy harvesting work in a field where napping and lodging are mixed. Is.
[0007]
[Means for Solving the Problems]
[Configuration, Action and Effect of Invention of Claim 1]
[0008]
According to the first aspect of the present invention, there is provided a combine transmission structure configured such that the crawler traveling device is driven by a continuously variable transmission, and the cutting operation unit is driven by another continuously variable transmission, so A control device that controls the shift of the continuously variable transmission of the working system in conjunction with a shift operation of the continuously variable transmission of the traveling system so that the driving speed of the working unit has a predetermined predetermined characteristic is provided. Two types of modes, “napping mode” and “inclination mode”, are pre-stored as the relationship characteristics with the mowing operation unit drive speed, and both modes are selected manually and the selected mode is maintained. And temporarily switching to the other mode different from the mode selected by the cutting mode selection means only while operating the operation tool. Wherein the are provided with a stage.
[0009]
According to the above configuration, the harvesting mode selection unit is set to “puffed mode” in a field with many napped crops, and the harvesting mode selection unit is set to “slung mode” in a field with many lying crops. And, for example, if you enter a local lodging area while working in the “napping mode”, you can temporarily switch to the “lodging mode” by continuing to operate the operation tool, By releasing the operation of the operation tool, it is possible to return to the original work in the “napping mode”. On the other hand, if you enter the local raised area during work in the `` lodging mode '', you can temporarily switch to the `` napped mode '' only during that time by continuing to operate the operation tool. By releasing the operation of the operation tool, it is possible to return to the original work in the “slave mode”.
[0010]
Therefore, according to the first aspect of the present invention, it is possible to temporarily switch the pre-selected mowing mode to the reverse mowing mode simply by continuing to operate the operation tool. The harvesting and harvesting can be performed lightly and easily, and even an inexperienced worker can efficiently perform the harvesting and harvesting work in a field where napping and lodging are mixed.
[0011]
[Configuration, Action and Effect of Invention of Claim 2]
[0012]
According to a second aspect of the present invention, there is provided a transmission mechanism for a combine according to the first aspect, wherein the operating tool for operating the mowing mode temporary switching means is gripped by a main transmission lever for operating the continuously variable transmission of a traveling system. The part is equipped with finger operation.
[0013]
According to the above configuration, the chopping mode can be temporarily switched with the finger of the hand operating the main speed change lever while arbitrarily changing the traveling speed by grasping the main speed change lever, and there is no need to change the lever. Traveling speed change and cutting mode switching can be performed, and the above effect of the invention of claim 1 is brought about and handling becomes easy.
[0014]
[Configuration, Action and Effect of Invention of Claim 3]
[0015]
According to a third aspect of the present invention, there is provided the combine transmission structure according to the second aspect, wherein the operating tool is pushable on the front surface of the grip portion of the main transmission lever that is swung back and forth.
[0016]
According to the above configuration, in a normal speed change operation, the main speed change lever is swung back and forth by gripping the grip part of the main speed change lever from above, and the operating tool provided in front of the grip part The operation mode can be temporarily switched during the pressing operation by consciously pressing the operation tool with the fingertip, and the above effect of the invention of claim 2 can be achieved. Further encourage.
[0017]
DETAILED DESCRIPTION OF THE INVENTION
FIG. 1 shows the entire side surface of the self-removing combine according to the present invention. The basic structure of this combine is not particularly different from the conventional one, and a multi-cutting mowing operation unit 3 is driven ascending and descending as a harvesting operation unit at the front of a traveling machine body 2 equipped with left and right crawler traveling devices 1. In addition to being connected to each other, on the right side of the front part of the traveling machine body 2, there is provided a control unit 6 in which an engine 5 is installed below the driver's seat 4. In addition to being mounted, a grain recovery tank 9 having a screw-type unloader 8 is provided on the right side. The mowing operation unit 3 includes a plurality of pulling device 11, a clipper type mowing device 12, and a mowing cereal basket on a mowing working unit frame 10 supported on the front portion of the traveling machine body 2 so as to swing up and down around a fulcrum X. Is provided with a cereal conveying device 14 that conveys the raw material toward the feed chain 13 of the threshing device 7, and the entire mowing operation unit 3 is driven up and down by a hydraulic cylinder 15.
[0018]
The present invention is characterized by the transmission structure to the crawler traveling device 1 and the mowing unit 3, and the following detailed configuration will be described based on the drawings.
[0019]
FIG. 2 is a schematic configuration diagram of the transmission structure as viewed from the front of the machine body, and FIG. 3 is a longitudinal front view of the mission case 20. In these figures, a pair of hydraulic continuously variable transmissions (HSTs) 21 for independently driving the left and right crawler travel devices 1 are provided on one lateral side of the transmission case 20 (the right lateral side with respect to the aircraft). 22 and a hydraulic continuously variable transmission (HST) 23 that drives the cutting work unit 3. Further, an input shaft 24 projects from the other lateral surface of the mission case 20 (the left lateral surface with respect to the aircraft), and the input shaft 24 and the engine 5 are interlocked with a belt.
[0020]
Each of the continuously variable transmissions 21, 22, and 23 has axial plunger type variable displacement pumps P (1), P (2), and P (3) in a casing part integrally projecting from the right side wall of the transmission case 20, respectively. And constant capacity type motors M (1), M (2), M (3) are installed, and port blocks 21c, 22c, 23c for hydraulic control are attached to the outer end of the case. The power that has entered the shaft 24 is transmitted from the counter gear G1 to the pump shafts 21a and 22a of the continuously variable transmissions 21 and 22 of the traveling system via the gears G2 and G3, and is also transmitted to the working system via the gear G4. It is transmitted to the pump shaft 23a of the continuously variable transmission 23. Each motor shaft 21b is operated by changing the swash plate angle of each variable displacement pump P (1), P (2), P (3) and changing the discharge direction and discharge amount of the pressure oil. , 22b and 23b can be switched between forward and reverse rotations and continuously variable from zero speed.
[0021]
The speed change output from the motor shaft 21b of the continuously variable transmission 21 is transmitted to the first intermediate shaft (left) 26 via the gear-type sub-transmission mechanism (left) 25 and then to the second intermediate shaft 27. The left crawler traveling device 1 is driven by being transmitted to the axle (left) 29 via the gear reduction mechanism 28 that is loosely supported. Further, the shift output from the motor shaft 22 b of the continuously variable transmission 22 is transmitted to the first intermediate shaft (right) 31 via the gear-type sub-transmission mechanism (right) 30 and then to the second intermediate shaft 27. The right crawler traveling device 1 is driven by being transmitted to the axle (right) 33 through the loosely supported gear reduction mechanism 32.
[0022]
The auxiliary transmission mechanism (left) 25 is a pair of gears loosely fitted to the large and small gears G5, G6 and the first intermediate shaft (left) 26 driven by the motor shaft 21b and meshed with the gears G5, G6. G7 and G8, a transmission boss 35 splined to the first intermediate shaft (left) 26 between both gears G7 and G8, and a shift sleeve 36 externally fitted to the transmission boss 35 are provided in a constant mesh form. The shift sleeve 36 is configured so as to be capable of shifting in two steps of high and low, and the shift sleeve 36 is shifted so as to mesh between the transmission boss 35 and the boss of the gear G8, so that "low speed" is obtained. “High speed” is obtained by shifting so as to mesh over the boss of G7, and when the shift sleeve 36 is positioned on the transmission boss 35 and the engagement with the bosses of both gears G7 and G8 is released, Thereby making it possible to bring the neutral ".
[0023]
The auxiliary transmission mechanism (right) 30 is also configured to have the same specifications as the auxiliary transmission mechanism (left) 25, and has large and small gears G9 and G10 driven by a motor shaft 22b and a first intermediate shaft (right) 31. A pair of gears G11 and G12 engaged with the gears G9 and G10, a transmission boss 37 splined to the first intermediate shaft (right) 31 between the gears G11 and G12, and a transmission The shift sleeve 38 is externally fitted to the boss 37 by a spline. By shifting the shift sleeve 38 so as to engage the transmission boss 37 and the boss of the gear G12, "low speed" is obtained. “High speed” is obtained by shifting so as to mesh between the transmission boss 37 and the boss of the gear G11, and the shift sleeve 38 is positioned on the transmission boss 37 to engage the bosses of both the gears G11 and G12. Solution If you divide, you can bring "neutral".
[0024]
As shown in FIG. 4, the pair of shift forks 40 and 41 engaged with the shift sleeves 36 and 38 of the both sub-transmission mechanisms 25 and 30 have a common shift shaft supported by the transmission case 20 so as to be movable left and right. The shift shaft 42 is configured to be driven and shifted by a speed change operation cylinder 43 assembled to the transmission case 20, and the shift shaft 42 is selectively moved to three positions by the speed change operation cylinder 43. Thus, both the sub-transmission mechanisms 25 and 30 are switched to “low speed” for work travel, “high speed” for mobile travel, or “neutral”.
[0025]
A piston rod 44 connected to the shift shaft 42 and a ring-shaped piston 45 fitted and supported by the shift shaft 42 are incorporated in the speed change operation cylinder 43, and the piston rod is moved to three positions by controlling the pressure oil supply pattern. It is possible to move out and in. That is, as shown in FIG. 7, the speed change operation cylinder 43 is connected to a pair of electromagnetic opening and closing valves 46 and 47, and the switch mechanism SW that detects the operation position of the auxiliary speed change lever 48 provided in the control unit 6. Based on the detection result, switching control is performed as follows.
[0026]
That is, when the auxiliary transmission lever 48 is in the neutral position, as shown in FIG. 7 (a), both the electromagnetic opening / closing valves 46, 47 are in a non-excited state, and both the electromagnetic opening / closing valves 46, 47 are both opened. Thus, pressure is applied to the two pressure oil ports a and b of the speed change operation cylinder 43, and the piston rod 44 is retreated in the left direction in the figure by the pressure from the pressure oil port a. The piston rod 44 is moved to the limit in the right direction in the figure by the pressure from the pressure oil port b, and the piston rod 44 is held at the neutral position restricted by the ring-shaped piston 45 due to the difference in pressure receiving area. When the auxiliary transmission lever 48 is operated to the “low speed” position, as shown in FIG. 7 (b), only one electromagnetic opening / closing valve 47 is energized and the pressure oil port a is communicated with the tank. The piston rod 44 and the ring-shaped piston 45 are moved to the limit in the right direction in the figure by the pressure from the oil port b, and the piston rod 44 is advanced to the “low speed” for working travel. Further, when the auxiliary transmission lever 48 is operated to the “high speed” position, as shown in FIG. 7C, only one of the electromagnetic on-off valves 46 is energized and excited, and the pressure oil port b is communicated with the tank. The piston rod 44 is moved to the limit in the left direction in the figure by the pressure from the oil port a, and the piston rod 44 is retracted to the “high speed” for moving travel.
[0027]
The first intermediate shaft (left) 26 is supported over the left and right side walls of the transmission case 20, while the first intermediate shaft (right) 31 is loosely supported by the first intermediate shaft (left) 26. In addition, a multi-plate linear clutch 50 that is hydraulically operated is interposed between the first intermediate shaft (left) 26 and the first intermediate shaft (right) 31. The straight clutch 50 is engaged when the left traveling continuously variable transmission 21 and the right traveling continuously variable transmission 22 are both operated in the same direction in the same direction, that is, in the straight operation state, the clutch is engaged. Even if the first intermediate shaft (left) 26 and the first intermediate shaft (right) 31 are integrated and the output rotational speeds of both continuously variable transmissions 21 and 22 are slightly different, the axle (left) 29 and the axle (Right) 33 is driven at the same speed, and a straight traveling state is surely brought about. Further, when the operation of the continuously variable transmission 21 for the left traveling and the continuously variable transmission 22 for the right traveling is not the same, that is, when the steering operation of the fuselage is performed, the linear clutch 50 is operated to be disconnected. In addition, the linear clutch 50 is controlled to operate in conjunction with the steering operation.
[0028]
As shown in FIG. 4, the linear clutch 50 includes a large-diameter drum 51 fixed to the first intermediate shaft (left) 26 and a small-diameter drum 52 fixed to the end portion of the first intermediate shaft (right) 31. Pressure oil supplied through oil passages c and d in the shaft is provided with a friction plate 53 interposed therebetween and a piston member 54 incorporated between the first intermediate shaft (left) 26 and the large-diameter drum 51. The clutch engaging / disengaging operation is configured to be engaged or disengaged by forward or reverse operation of the clutch, and the clutch engaging operation oil passage c and the clutch disengaging operation oil passage d are electromagnetically connected via a rotary joint 55 attached to the shaft end. It is connected to the open / close valves 56 and 57 [see FIG. 7].
[0029]
Further, an inwardly expanding brake 58 is mounted on the end portion of the first intermediate shaft (left) 26, and a ring-shaped spring 59 that presses and urges the piston member 54 in the clutch engagement direction is attached to the linearly-moving clutch 50. In a state in which a plurality of sheets are assembled and no pressure is applied to any of the oil passages c and d, the friction plate 53 is elastically pressed by the spring 59 and the linear clutch 50 is lightly connected. Has come to be brought.
[0030]
Accordingly, when switching from the straight traveling state to the turning state, or when returning from the turning state to the straight traveling state, a state in which no pressure is generated in both the oil passages c and d is revealed for a very short time. 29 and 33 are brought into a lightly connected state via the straight clutch 50, and the occurrence of a shock at the start of turning and a shock when returning from turning to straight running is suppressed.
[0031]
When the aircraft is parked, the engine 5 is stopped and the brake 58 is applied. However, when the engine 5 is stopped, the oil passages c and d are not pressurized, so the piston member 54 is free. As a result, the straight clutch 50 is disengaged and the brake 58 acts only on the first intermediate shaft (left) 26 and only the left crawler traveling device 1 is braked. Since the first intermediate shaft (left) 26 and the first intermediate shaft (right) 31 are in an appropriate frictional transmission state via the spring 59, the braking action acting on the first intermediate shaft (left) 26 is the first intermediate shaft. (Right) 31 also extends to some extent, and even when parked on a slope, it is avoided that the crawler traveling device 1 on the right side is in a free state and the aircraft is steered by its own weight. It is like that.
[0032]
As shown in FIGS. 2 and 3, the shift output from the motor shaft 23 b of the continuously variable transmission 23 of the work system is a work output shaft (PTO shaft) protruding from the left lateral surface of the transmission case 20. 60 is transmitted through gears G12 and G13, and is transmitted to the mowing unit 3 via a belt tension type mowing clutch (not shown).
[0033]
FIG. 6 shows a hydraulic circuit relating to the continuously variable transmissions 21, 22, and 23. The variable displacement pumps P (1) and P (2) of the continuously variable transmissions 21 and 22 in the traveling system are shifted by servo cylinders 63 and 64 that are controlled by the valve units 61 and 62, respectively. Yes. Each valve unit 61, 62 is configured by combining a pair of normally closed type electromagnetic on-off valves 65, 66 and a pair of normally open type electromagnetic on-off valves 67, 68. As shown in FIG. Both valve units 61 and 6 are connected to a control device 70 and controlled as described later.
[0034]
A charge pump CP (1) for supplying charge pressure oil to the charge circuits e and f of both continuously variable transmissions 21 and 22 is mounted on the pump shaft 22a of one continuously variable transmission 22 of the traveling system. A charge pump CP (2) for supplying charge pressure oil only to the charge circuit g of the continuously variable transmission 23 is mounted on the pump shaft 23a of the continuously variable transmission 23 of the working system. Here, the pressure oil from the charge pump CP (1) is also supplied to valve units 61 and 62 for shifting the traveling continuously variable transmissions 21 and 22, that is, a hydraulic servo system to which a load is applied. For this reason, the charge pump CP (1) has a larger discharge amount than the charge pump CP (2), and the charge relief valves CR (1) and CR (2) are used for the charge circuit e, The pressure of f is set to be higher than the pressure of the charge circuit g in the work system.
[0035]
Further, the casings of the traveling continuously variable transmissions 21 and 22 are connected to each other by a pipe h in the case, and the drain oil from the continuously variable transmission 21 in the left traveling system is connected to the right traveling system through the casing h. After flowing into the casing of the step transmission 22, it is taken out via the external drain pipe i, and collected in a dedicated hydraulic oil tank T via the oil cooler OC. Further, the drain oil of the continuously variable transmission 23 of the working system is also collected in the hydraulic oil tank T via the external drain pipe j and the oil cooler OC.
[0036]
Next, the operation of the hydraulic servo system that operates the continuously variable transmissions 21 and 22 will be described. Since both hydraulic servo systems have the same specifications, the operation will be described using the hydraulic servo system of one continuously variable transmission 21.
[0037]
A pair of return springs 69 are incorporated in the servo cylinder 63, and as shown in FIG. 8 (a), when all the electromagnetic on-off valves 65 to 68 are in a non-energized state, the servo cylinder 63 has both return springs 69. To return to the neutral position. Then, as shown in FIG. 8B, one normally closed electromagnetic switching valve 65 is energized and opened, and one normally open electromagnetic switching valve 67 is energized and closed, so that the charge pump CP (1 ) Is supplied to the oil passage m (oil passage n in the servo cylinder 64), and the servo cylinder 63 operates from the neutral position to the forward side. Then, as shown in 8 (c), when the servo cylinder 63 is operated forward, the energization of the normally closed electromagnetic on-off valve 65 is stopped and returned to the closed position. Is prevented and the servo cylinder 63 is held in its forward position.
[0038]
Conversely, as shown in FIG. 8 (d), the other normally closed electromagnetic on-off valve 66 is energized and the other normally open electromagnetic on / off valve 68 is energized, so that the charge pump CP ( The pressure oil from 1) is supplied to the oil path q (oil path r in the servo cylinder 64), and the servo cylinder 63 operates from the neutral position to the reverse side. Then, as shown in FIG. 8 (e), when the normally closed electromagnetic on-off valve 66 is de-energized and returned to the closed position after the servo cylinder 63 is operated to the reverse side, the pressure oil from the oil path q is restored. The outflow is prevented and the servo cylinder 63 is held in the backward position.
[0039]
The valve units 61 and 62 are feedback-controlled in accordance with the operation positions of a single main transmission lever 71 provided in the control unit 6 that can swing back and forth and a single steering lever 72 that can swing left and right. The control will be described below.
[0040]
As shown in the block diagram of FIG. 9, the operation position of the main transmission lever 71 and the operation position of the steering lever 72 are detected by potentiometers PM (1) and PM (2), respectively, and both continuously variable transmissions are detected. The operation positions (swash plate angles) of the variable displacement pumps P (1) and P (2) in 21 and 22 are detected by the potentiometers PM (3) and PM (4) and fed back to the control device 70. The target shift positions of the continuously variable transmissions 21 and 22 are determined by the operation position of the main shift lever 71 and the operation position of the steering lever 72, and the shift by feedback control is performed toward the target shift position. Done. The electromagnetic on-off valves 56 and 57 for linear clutch control are energized as described above based on the steering state detected by the potentiometer PM (2).
[0041]
When the main shift lever 71 is operated from neutral to forward or backward, the same target shift position corresponding to the amount of operation is set in both continuously variable transmissions 21 and 22, and the variable displacement pumps P (1) and P (2) Are operated forward or backward until they reach the target shift position, and are held at the target shift position. As a result, it is possible to perform forward / reverse shifting in a straight line. In addition, when the steering lever 72 is operated from the neutral position to the left (or right) from the forward or reverse straight traveling state, the left traveling continuously variable transmission 21 (or the right traveling continuously variable transmission). 22) the target shift position is corrected in the deceleration direction, deceleration control is performed toward the corrected target shift position, and the aircraft is strengthened according to the lever operation amount in the direction in which the steering lever 66 is operated. It is linked so that it may turn with the turning function.
[0042]
For example, when the steering lever 72 is operated to the left while the vehicle is moving straight forward at the speed set by the main transmission lever 71, the one continuously variable transmission 21 is decelerated and the forward speed of the crawler traveling device 1 on the left side is reduced. The aircraft will turn to the left due to the difference in speed between the left and right sides. Then, when the steering lever 72 is largely operated to the left and the one continuously variable transmission 21 is decelerated to the neutral position, the left crawler traveling device 1 on the inner side of the turn is stopped and the belief turn is performed. . Further, when the steering lever 72 is further operated to the left, one continuously variable transmission 21 is shifted to the reverse side beyond the neutral position, and the left crawler traveling device 1 on the inside of the turn is reversed. This is a super-sounding turn.
[0043]
As shown in FIG. 9, the variable displacement pump P (3) of the continuously variable transmission 23 that controls the cutting work unit 3 is operated by an actuator 73 such as an electric motor, and the forward travel speed Va. In relation to the forward shifting operation of the main transmission lever 70 so that the relationship between the cutting speed and the cutting portion drive speed Vb becomes a characteristic preset by map data or the like. The position is automatically determined, and the continuously variable transmission 23 is feedback-controlled toward the target shift position. The speed change position of the continuously variable transmission 23 is detected by the potentiometer PM (5) as the operation position (swash plate angle) of the variable displacement pump P (3).
[0044]
As shown in FIG. 10, the relationship between the forward travel speed Va and the mowing operation unit drive speed Vb is “a napped mode” in which the mowing operation unit drive speed Vb changes substantially linearly with respect to the change in the forward travel speed Va. The cutting operation unit driving speed Vb is set to two types of cutting modes, “falling mode” in which the cutting operation unit driving speed Vb rises significantly in the low speed range and decreases less in the high speed range. Any of the cutting modes can be selected by the cutting mode selection switch S (1) as the selection means.
[0045]
In addition, when the napping mode temporary changeover switch S (2) is turned on while the “napping mode” or the “inclination mode” is selected by the mowing mode selection switch S (1), the mowing is performed only during the turning operation. When the other cutting mode different from the cutting mode selected by the mode selection switch S (1) is set and the on / off operation of the temporary cutting mode switch S (2) is canceled, the cutting mode selection switch S (1) is selected. It returns to the original mowing mode.
[0046]
As shown in FIG. 12, the reaping mode temporary changeover switch S (2) is configured to be operated by a push button 74 as an operation tool provided on the front surface of the grip portion 71a of the main transmission lever 71. The mowing mode temporary changeover switch S (2) is turned on and operated by lightly pressing the push button 74 with the middle finger or the like of the left hand placed so as to cover the grip 71a of the main transmission lever 71.
[0047]
Therefore, in the field with many napped crops, the cutting mode selection switch S (1) is set to “Napping mode”, and in the field with many lying crops, the cutting mode selection switch S (1) is set to “Striking mode”. Do work. And, for example, when entering the local lodging area during the work in the “napped mode”, the push button 74 of the main speed change lever 71 can be continuously operated, so that it can be temporarily switched to the “lodging mode” only during that time. When the user falls out of the lying area, the operator can return to the original work in the “napping mode” by releasing the finger from the push button 74. On the other hand, when entering the local raised region during work in the “liedown mode”, by continuing to push the push button 74, it is possible to temporarily switch to the “raised mode” only during that time. When released, the finger can be released from the push button 74 to return to the original work in the “inclination mode”.
[0048]
The present invention can also be carried out by being modified into the following forms.
(1) The left and right crawler traveling devices 1 may be driven by a single hydraulic continuously variable transmission.
(2) The continuously variable transmission of the traveling system and the working system can be implemented by a belt type or other mechanical type.
[Brief description of the drawings]
[Fig. 1] Overall side view of the self-removing combine as seen from the left side of the fuselage [Fig. 2] Front view showing the schematic configuration of the transmission structure [Fig. 3] Vertical front view of the transmission case [Fig. Front view [Fig.5] Side view of the shaft arrangement of the transmission case as seen from the left side of the fuselage [Fig.6] Hydraulic circuit diagram [Fig.7] Hydraulic circuit diagram for operating the sub-transmission mechanism and linear clutch [Fig.8] Each servo cylinder FIG. 9 is a block diagram showing the control system of the continuously variable transmission. FIG. 10 is a characteristic diagram showing the relationship between the running speed and the mowing operation unit driving speed. [Fig. 12] Perspective view of main transmission lever [Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Crawler traveling apparatus 3 Cutting work part 21 Continuously variable transmission 22 Continuously variable transmission 23 Continuously variable transmission 71 Main transmission lever 71a Grip part 74 Operating tool (push button)
S (1) Mowing mode selection means (switch)
S (2) Mowing mode temporary switching means (switch)
Va Traveling speed Vb Cutting speed of cutting section

Claims (3)

The crawler traveling device is configured to be driven by a continuously variable transmission, and the mowing working unit is configured to be driven by another continuously variable transmission,
Provided with a control device for controlling the shift of the continuously variable transmission of the working system in conjunction with the shifting operation of the continuously variable transmission of the traveling system so that the traveling speed and the driving speed of the cutting working unit have a predetermined predetermined characteristic. ,
As for the relational characteristics between the running speed and the cutting unit driving speed, two types of modes, “Napping mode” and “Laying mode”, are stored in advance, and both relational characteristics are selected artificially, and the selected mode is maintained . A cutting mode selection means,
A combine transmission structure characterized by comprising a mowing mode temporary switching means for temporarily switching to the other mode different from the mode selected by the mowing mode selection means only while operating the operating tool.   The combine transmission structure according to claim 1, wherein the operating tool for operating the mowing mode temporary switching means is provided so as to be operated by a finger on a grip portion of a main transmission lever that operates the continuously variable transmission of a traveling system.   The combine transmission structure according to claim 2, wherein the operation tool is provided so as to be pressed on a front surface of a grip portion of the main transmission lever that is swingably operated back and forth.

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