KR101603347B1 - Reaping-harvesting machine - Google Patents

Abstract

In addition to the high-speed driving range of Noh Sang-Yong and the medium speed range suitable for cutting work, there is a control panel which can select even a low-speed driving range suitable for cutting stems and culms (hereinafter referred to as " A cut-off harvester is disclosed in which the possibility of operation is small and the layout space is also small. In this shearing machine, both the hydraulic pump 41 and the hydraulic motor 42 constituting the hydrostatic stepless transmission 4 are of a variable capacity type. In the speed control area by the hydraulic motor 42, (Hereinafter referred to as "standing spindle"), and a low-speed running area suitable for the cutting operation of the coated span at a speed lower than the running speed in the medium-speed running area A first operating member 23 for selectively switching the high-speed traveling region and the middle-speed traveling region by setting the traveling region, a second operating member 24 for selectively switching the middle-speed traveling region and the low- Respectively.

Description

{REAPING-HARVESTING MACHINE}

The present invention relates to a crop harvesting machine such as a combine harvester.

[1] It is known that a combine having a hydrostatic stepless speed changer has a structure described below.

That is, each of the hydraulic pump and the hydraulic motor of the hydrostatic stepless speed change device is of a variable capacity type, and the hydraulic pump is shifted by the operation of the peripheral speed lever, and a push button switch for high speed traveling, And the push button switch for running the clothes, respectively, so as to control the operation of the hydraulic motor so as to perform the shift control so that the traveling output becomes a traveling speed suitable for each of the high speed traveling, middle speed traveling and low speed traveling phases (See paragraphs [0031], [0035], FIGS. 2, 3, 4, and 9 of JP-A-2005-265052).

2 and 4 in JP-A-2005-265052), a hydraulic pump (not shown) of a hydrostatic stepless speed changer is provided in the combine harvester, Fig. 2 of JP-A-2005-265052 and 13 of Fig. 4) are configured to be able to change steplessly to the forward side and the reverse side.

In JP-A-2005-265052, a hydraulic motor (equivalent to a transmission for traveling) of a hydraulic motor of JP-A-2005-265052 is operated at a high speed position, a middle speed position and a low speed position (JP-A-2005-265052, FIGS. 3 and 4 in FIGS. 3 and 4, 33, and 4), and the hydraulic motor of the hydrostatic stepless speed changer is configured separately from the hydraulic pump of the hydrostatic stepless transmission. 34, 35).

In this case, in the hydraulic motor of the hydrostatic stepless speed changer, a high-speed position is used for running on a road or a slat, and medium-speed position is used for cutting work in agricultural land. In the cutting work on agricultural land, If the area of severe wear is reached, operate the hydraulic motor of the hydrostatic stepless speed changer to the low speed position.

In the case of cutting such heavy crops, it is possible to prevent the state in which the cutting speed due to the pre-installation part is not made in time because the running speed of the gas is too fast with respect to the operating speed of the pre- , And the overturned crop can be cut without delaying the cutting.

[3] In addition, combin, which is an example of a cut-off harvester, includes a running vehicle and a cut-off winding system as disclosed in JP-A-2004-187506.

Here, the power of the engine (8 in Fig. 2 of JP-A-2004-187506) is transmitted to the hydrostatic stepless speed changer (7 in Fig. 2 of JP-A-2004-187506) (7b in Fig. 2 of JP-A-2004-187506) is branched in parallel to the traveling electric machine and the shearing electric machine. The driving force of the traveling vehicle is transmitted to the traveling device (1 in Fig. 1 and Fig. 2 of JP-A-2004-187506) through the auxiliary transmission (JP-A-2004-187506, The power of the electric power system is transmitted to the preload part (2 of Fig. 1 and Fig. 2 of JP-A-2004-187506) through the cutting transmission (15 of Fig. 2 of JP-A-2004-187506).

Generally, in the cutting and harvesting machine, when the running speed of the gas is synchronized with the running speed of the preloading portion (when the running speed of the gas is low, the running speed of the preloading portion is low, And the operating speed is also high). Therefore, if the cutting transmission is fixed to a predetermined shift position in JP-A-2004-187506, the running speed of the base and the operating speed of the preload are tuned by operating the hydrostatic stepless speed changer The speed change device is generally provided with a high speed position for traveling on a road or a slope, and is provided with a low speed position for cutting work in agricultural land, so that the auxiliary speed change device is not operated at a high speed position during the cutting operation. The transmission is fixed at a low speed position).

[1] Problems to be solved in the background art [1] are as follows.

JP-A-2005-265052 discloses a structure in which a hydraulic pump is shifted by an operation of a peripheral speed lever and a work speed is changed by a hydraulic motor with a plurality of pushbutton switches, So that the vehicle can be driven at a speed suitable for a desired operation and can be conveniently used.

However, in the structure described in Patent Document 1, a desired work traveling speed is obtained by selectively operating the above-mentioned push button switch for high speed traveling, push button switch for medium speed traveling, and push button switch for low speed traveling, respectively So, there are the following problems.

That is, as the number of push buttons used as the manipulation sphere increases, it becomes easy to select a speed near the speed range suitable for a desired operation as a selection target. On the other hand, when the number of selection objects increases, It is likely to be easy.

In order to avoid such erroneous operation, countermeasures such as an extremely large arrangement interval of the push-button switches are considered. However, even if this is done, There is a problem that the space for disposal of the space becomes extremely large and waste of space occurs.

It is an object of the present invention to provide an apparatus and a method for controlling a running speed of a running sprung sprue in a high speed running region suitable for running on a hearth or an intermediate speed running region suitable for cutting an upright span, The possibility of erroneous operation is small and the arrangement space of the operation tool is also minimized.

[2] Problems corresponding to the background art [2] are as follows.

In the cutter harvester, as disclosed in JP-A-11-032557 (see Figs. 2 and 22), there is also a machine equipped with a transmission for cutting. Thus, it is conceivable to combine a transmission for a cut-off part with a cut-off harvester which can set the traveling speed of the gas to a low speed when cutting crops with heavy clothing.

The present invention relates to a cutting and harvesting machine in which, when the traveling transmission is configured to be operable at a high speed position for traveling, at a medium speed position for cutting work, and at a low speed position for clothes cutting work, Speed transmission device of the present invention.

[3] Problems to be solved in the background art [3] are as follows.

In the shearing machine, the hydraulic pump of the hydrostatic stepless speed change unit is configured to be continuously variable from the forward side to the reverse side to operate the hydraulic pump of the hydrostatic stepless speed changer to perform forward and backward operations of the gas, So that many operations are performed. Thereby, when the cropping of the crop reaches a severe part in the cutting work in the agricultural land, the hydraulic pump of the hydrostatic stepless transmission is operated to the low speed side to operate the running speed of the gas at low speed.

However, operating the hydraulic pump of the hydrostatic stepless speed change unit to the low speed side reduces the discharge amount of the hydraulic pump of the hydrostatic stepless speed change unit, so that the running speed of the base is low and the driving force (torque) is also small. Thus, it can be considered that the driving force (torque) becomes insufficient when the hydraulic pump of the hydrostatic stepless speed changer is operated to the low speed side in a weak farmland with a large running resistance.

An object of the present invention is to provide a structure in which the traveling speed of the gas can be lowered while avoiding a decrease in the driving force (torque) when the hydrostatic stepless speed changer is provided in the cutting and harvesting machine.

[1] Means for solving the problem [1] are as follows.

That is, in a combine having a constant-hydraulic-type continuously-variable transmission device for shifting the power input from the engine side to the traveling device side,

Wherein the hydraulic pump and the hydraulic motor constituting the hydrostatic stepless transmission are both of variable capacity type,

And the forward / backward movement of the base is performed in the continuously-variable shifting state by the shifting operation by the hydraulic pump,

A high speed running region suitable for running on the hearth in the speed control region by the hydraulic motor, an intermediate speeding region suitable for cutting the upright span in the farmland, and a low speed span of the running span at a speed lower than the traveling speed in the medium speeding region Setting a low-speed running region suitable for the work,

And a second operating port for selectively switching over between the high speed traveling region and the medium speed traveling region and the medium speed traveling region and the low speed traveling region, do.

With this configuration, the gas is forwardly and rearwardly shifted in the continuously-variable shifting operation by the hydraulic pump, and the speed control region by the hydraulic motor is provided with a high-speed running region suitable for running on the road, Speed running region suitable for the cutting work of the span span at a lower speed than the running speed in the medium speed running region is set in a wide range extending from the running of the road to the cutting work of the span span The work speed adapted to the speed change of the work speed can be selected.

In particular, according to the present invention, it is preferable that a first operating member for selectively switching over between the high-speed running region and the medium-speed running region, and a second operating member for selectively switching the medium- Therefore, it is possible to change the operation speed of the combine to the desired working speed among the operation modes of the combine by alternatively switching the first operating opening, selectively operating the second operating opening, Operation becomes possible.

That is, in the combine, when running in a high-speed running region suitable for running on the hearth, there is little need to perform the shifting operation from the running state to the low-speed running region that is suitable for the cutting operation A normal shifting operation is performed between the medium speed running region and the high speed running region suitable for the cutting operation of the upright spindle in the agricultural land so as to perform the normal upright span cutting operation and the shifting operation for selecting the running form by the running in the non- Is desired.

Further, when traveling in a low-speed running region suitable for the cutting work of the sprocket span, it is not necessary to perform the shifting operation from the running state to the high-speed running region suddenly suitable for running on the road, Speed shifting operation is performed between the medium speed running region and the low speed running region suitable for the cutting operation and the shifting operation for switching the traveling pattern to the low speed traveling mode, taking the span of the normal state as an example, Is desired.

When the vehicle is traveling in the middle speed range suitable for the cutting operation of the upright span to the agricultural land, there is a possibility that the shift operation is performed to any of the above-mentioned high speed range and low speed range. However, It is judged whether the frequency of shifting between the low speed traveling region and the low speed traveling region is large and whether the operation by the first operating section should be performed or not by the second operating section It is possible to select whether to perform the operation.

As a result, in the present invention, as an operator for selecting a working speed, it is possible to use only one of the above-described first operating opening and the second operating opening, so that a high-speed driving region suitable for running on the road and a straight- Speed running area suitable for the cutting work of the span span can be selected.

Therefore, since the desired operation speed can be selected by the above-described first operation opening and the second operation opening, it is possible to reduce the possibility of causing a false operation as compared with the operation of selecting any one of the many operation opening .

In addition, since there is no need for a large number of operation ports and there is less possibility of causing erroneous operation, a large occupied space is not required as a space for disposing the operation ports, and there is an advantage that a compact overall structure can be obtained .

In one embodiment, the present invention is characterized in that, when the second operating member is switched to the low-speed running region, there is provided an operating means for shifting the speed change gear in the driveline of the pre-load portion at high speed.

According to the above configuration, in a state in which the second operating opening is switched to the low-speed running region, a driving form suitable for cutting work in a covered state due to a large span to be cut is required. Under these working conditions, it is necessary to sufficiently reduce the running speed of the base so as to avoid drawing out a largely overlapped span, and at the same time to increase the amount of operation to be generated.

Therefore, the above-mentioned second operating port is switched to the low-speed running region to greatly reduce the running speed of the base so as to enable the cutting of the clothes, and accordingly, the working machine is shifted at high speed, So that the amount of generation is increased. As a result, there is an advantage that it is possible to satisfactorily perform the job of cutting the clothes.

In a preferred embodiment, the first operating section is provided on the grip of the shift operating lever for shifting the hydraulic pump of the hydrostatic stepless transmission, and the second operating section is provided on the steering panel.

According to the above configuration, the first operating opening for selectively switching the high-speed running region suitable for running on the hearth and the medium-speed running region suitable for the cutting operation of the upright span on the farmland is provided on the grip of the speed change operation lever, Since the second operating section for selecting and switching the traveling region and the low-speed traveling region suitable for the cutting operation of the coating springs at a lower speed than the traveling region is provided on the steering panel, the possibility of erroneously operating the first operating portion and the second operating portion is less There is an advantage that the possibility of avoidance of manipulation is higher.

Since the first operating opening for selectively switching the high speed running region suitable for running on the hearth and the medium speed running region suitable for the cutting operation of the upright span on the farmland is provided on the grip of the speed change operation lever, It is possible to perform a quick switching operation, and there is also an advantage in terms of improvement in work efficiency.

The second operating section for selecting and switching the middle speed traveling region suitable for the upright spindle work in the agricultural land and the low speed traveling region suitable for the cutting operation of the coating springs at a lower speed than the traveling speed in the middle speed traveling region is installed on the steering panel However, since the switching operation by the second operating member is not so high in operation frequency and the switching operation is also performed in a relatively low speed running state during straight running of the vehicle during the cutting operation, It is possible to continue the cutting work without any hindrance even if the control panel is removed.

In addition, since the second operating opening is provided on the steering panel, the second operating opening is displayed at a position where the second operating opening is always visible, so that it is convenient to return the switching operation without forgetting after the switching operation.

In a preferred embodiment, the hydrostatic stepless speed changer changes the inclined plate angle of the hydraulic motor to a single-acting cylinder (hereinafter referred to as " tilting ") that tilts the swash plate toward the high- And a return spring which contracts with the supply of the pressure oil and returns and pushes the single acting cylinder to the low speed output side as the pressure oil is discharged,

A high-speed output position in which the proportional pressure reducing valve is provided in the pressure supply passage into the hydraulic pressure chamber of the single-acting cylinder so that the single-acting cylinder compresses the return spring to a shrinkage limit, Speed output position is set at an intermediate position between the low-speed output position and the low-speed output position, and the intermediate-speed output position is set by supplying the pressurized oil in balance with the return-

Wherein the high speed output position of the hydraulic motor is a high speed running region suitable for running on the road and the medium speed output position is an intermediate speed running region suitable for the cutting operation of the upright span in the agricultural land and the low speed output position is higher than the running speed in the medium speed running region And is set in a low-speed running region suitable for cutting work at a low speed.

According to the above configuration, the means for setting the high-speed running region, the medium-speed running region and the low-speed running region by the hydraulic motor includes a single acting cylinder for changing the inclined plate angle of the hydraulic motor, Is obtained by setting the supply pressure applied to the single acting cylinder and the urging force of the return spring by using a return spring for returning and pushing the single acting cylinder to the low speed output side with the discharge of the pressure oil. There is an advantage that it can be simplified.

In other words, compared to a structure in which the position of the hydraulic piston for controlling the inclined plate angle of the hydraulic motor is detected and the piston position is controlled by a plurality of proportional control valves to thereby control the inclination plate angle, dedicated position detection means are not required, There is an advantage in that the number of valves used can be reduced and the structure can be simply configured.

[2] Means for solving the problem [2] are as follows.

That is, there is provided a traveling transmission, a transmission for a cutting unit, and an artificial manipulation member that is manipulated artificially. The traveling transmission is configured to be operable at a high speed position for traveling, at a middle speed position for cutting work, and at a low speed position for clothes cutting work, which takes a crop with heavy clothes.

A standard shifting state in which the shifting device for traveling is operated to the high speed position, the shifting device for shifting is operated to the medium speed position and the shifting device for the cutting device is operated to the low speed position, Speed shifting state in which the transmission for the cut-off part is operated to the high-speed position.

The artificial operation section, the shift device for traveling, and the shift device for the cut-off section are linked so as to be able to set the traveling state, the standard cutting state, and the low-speed cutting state by the artificial operation tool.

According to the above configuration, in the cutting work on the agricultural land, when the standard cutting state is set by the artificial operation tool, the traveling transmission is operated to the medium speed position, the transmission for the cut- The operating speed of the preload part is set to an appropriate value (for example, the running speed of the gas is set to an appropriate value with respect to the operating speed of the mounting part).

In this case, since the traveling transmission is operated to the intermediate speed position and the transmission for the cut-off part is operated to the low speed position by setting the standard cutting state by the artificial operating lever, the artificial operation And the artificial operation to the low speed position of the transmission for the cutting unit need not be performed individually.

In addition, when the cropping of the crop reaches a severe part in the cutting work in the agricultural land, if the low-speed cutting state is set by the artificial operation tool, the traveling transmission is operated to the low speed position and the transmission for the cut- Position.

In this case, since the traveling transmission is operated to the low-speed position, the traveling speed of the base relative to the traveling speed of the traveling part is suppressed, and the transmission for the traveling part is operated to the high speed, The operating speed of the preload portion is set to an appropriate value with respect to the running speed of the gas (the running speed of the gas is set to an appropriate value with respect to the operating speed of the preload portion) .

The transmission for traveling is operated to the low speed position and the transmission for the cut-off part is operated to the high speed position by setting the low speed cutting state by the artificial operation tool so that the artificial operation to the low speed position of the traveling transmission for traveling, It is not necessary to perform an artificial operation to the high-speed position of the shifting device for the secondary use.

In addition, when the traveling state is set by the artificial operation means in traveling on a road or a slat, the traveling transmission is operated to a high speed position, and traveling at a high speed on a road or a slope can be performed.

Therefore, in a case where the traveling transmission and the transmission for the cut-off part are provided in the cut-off harvester, the traveling transmission and the transmission for the cut-off part are appropriately linked to each other, State and low-speed cutting state can be set, so that it is possible to appropriately cope with the traveling cutting, the cutting work, and the clothes cutting work for taking crops with severe crops, thereby improving the workability of the cutting and harvesting machine.

It is also unnecessary to separately perform an artificial operation of the traveling transmission to the intermediate speed position and an artificial operation to the low speed position of the transmission for the cutting machine when the standard cutting state is set by the artificial operation tool, It is not necessary to perform an artificial operation to the low speed position of the transmission for traveling and an artificial operation to the high speed position of the transmission for the cut-off part when the low speed cutting state is set by the artificial operation tool, Can be improved.

In a preferred embodiment, a trim clutch is provided which is capable of transmitting and blocking power to the preload. And operating means for operating the cut-off clutch to a cut-off state when the running running condition is set. This configuration is more advantageous in the following respects.

Generally, in a cut-and-harvested harvester, traveling is often performed on a road or a slab in a state where the cut-off portion is stopped.

When the traveling running state is set by the artificial operation tool, the cut-off clutch is operated in the cut-off state to stop the cut-off portion, so that there is no need to carry out the artificial operation to the cut-off state of the cut-off clutch separately.

Therefore, when the moving running state is set by the artificial operation tool, it is not necessary to separately perform an artificial operation to the cutting state of the cutting clutch, and the operability of the cutting and harvesting machine can be improved.

In a preferred embodiment, the state in which the low-speed cutting state is set without inhibiting the standard cutting state from the traveling state is inhibited, and the state in which the traveling state is set without going through the standard cutting state from the low- And a checking means. This configuration is more advantageous in the following respects.

Since the traveling transmission is operated to the high speed position in the traveling state, and the transmission for traveling is operated to the low speed position in the low speed cutting state, there is a great difference in the travel speed of the vehicle in the traveling state and the low speed state.

In this configuration, when the running state is set from the low-speed cutting state to the low-speed cutting state, the traveling state can not be set without passing through the standard cutting state from the low-speed cutting state. After this, the traveling state must be set from the standard cutting state. Likewise, when the low-speed cutting state is set from the traveling running state by the artificial operation means, the low-speed cutting state can not be set from the traveling running state to the low-speed cutting state without going through the standard cutting state, You must set a low-speed cut condition from the standard cut condition.

Thus, when the running state is set from the low-speed cutting state to the low-speed cutting state by the artificial operation means and the low-speed cutting state is set from the traveling state by the artificial operation means, the traveling speed of the intermediate body between the traveling state and the low- When the running state is set from the low-speed cutting state to the low-speed cutting state (when the low-speed cutting state is set from the traveling running state to the low-speed cutting state by the artificial operation means) by the artificial operation shed, Can be suppressed.

Therefore, when the running state is set from the low-speed cutting state to the low-speed cutting state (when the low-speed cutting state is set from the traveling running state by the artificial operation sphere) by the artificial operation shed, the abrupt change in the running speed of the gas can be suppressed It is possible to prevent the deterioration of ride comfort due to a sudden change in the running speed of the vehicle.

In addition, since the operation of the traveling transmission device in which a sudden change in the traveling speed of the vehicle occurs is prevented, it is also advantageous in terms of improvement in the durability of the traveling transmission device.

[3] Means for solving the problem [3] are as follows.

That is, there is provided a constant-oil hydraulic step-variable transmission device to which the power of the engine is transmitted, and the hydrostatic type continuously variable transmission device is constituted by a hydraulic pump at the upper side of the electric motor and a hydraulic motor at the lower side of the electric motor. The hydraulic motor of the hydrostatic stepless speed change device is configured to be shiftable. The power of the hydraulic motor of the hydrostatic stepless speed change device is branched in parallel to the traveling electric motor and the shearing electric motor so that the power of the traveling electric motor is transmitted to the traveling device. The power of the cutting power transmission system is configured to be transmitted to the cutting section, and the cutting transmission system is provided with the cutting transmission. This configuration is advantageous in the following respects.

The operation of the hydraulic motor of the hydrostatic stepless speed change unit to the low speed side is intended to make the stroke of the plunger of the hydraulic motor of the hydrostatic stepless speed change unit small, so that even if the hydraulic oil is sufficiently supplied to the hydraulic motor from the hydraulic pump of the hydrostatic stepless speed change unit The hydraulic motor of the hydrostatic stepless speed changer does not have to rotate so much. Thus, when the hydraulic motor of the hydrostatic stepless speed changer is operated to the low speed side and the discharge amount of the hydraulic pump of the hydrostatic stepless speed changer is secured, sufficient driving force (torque) is transmitted downward from the hydraulic motor of the hydrostatic stepless speed changer, So that a low-speed power is transmitted.

According to the above feature, the power of the engine is transmitted to the traveling device through the hydraulic pump, the hydraulic motor, and the traveling electric motor of the hydrostatic stepless speed changer, and the hydraulic motor of the hydrostatic stepless transmission is configured to be shiftable.

Thus, when the hydraulic motor of the hydrostatic stepless speed changer is operated to the low speed side in a state in which the discharge amount of the hydraulic pump of the hydrostatic stepless speed change device is secured, low speed power having sufficient driving force (torque) is transmitted to the traveling device It is possible to obtain the traveling speed of the low-speed gas without the lack of the driving force (torque) even in a weak farmland with a large running resistance.

In addition, the power of the hydraulic motor of the hydrostatic stepless speed change device is branched in parallel to the traveling electric motor and the shearing electric motor to transmit the power of the traveling electric motor to the traveling device, and the power of the shearing electric motor is transmitted to the cut- have.

Thus, when the hydraulic motor of the hydrostatic stepless speed changer is operated, the power shifted by the hydraulic motor of the hydrostatic stepless speed changer is transmitted in parallel to the traveling device and the cut-off portion. Thus, like JP- A-2004-187506, A state in which the running speed of the base and the operating speed of the preload part are tuned is obtained.

In addition, in the case of the cropping work in the agricultural land, when the crop reaches the severe part, the running speed of the gas needs to be sufficiently low.

Thus, if the hydraulic motor of the hydrostatic stepless speed change unit is operated to the low speed side to sufficiently lower the running speed of the base, the operating speed of the preloading portion becomes sufficiently low (the operating speed of the preloading portion becomes too low) It is not possible to perform stable cutting in the attaching portion. (In the pre-attaching portion, stable cutting can not be performed unless an operating speed equal to or higher than a certain level is secured.)

On the other hand, in the present invention, when the hydraulic motor of the hydrostatic stepless transmission is operated to the low speed side and the traveling speed of the gas is sufficiently low because the shearing machine is provided with the shear transmission, the sheathed transmission is operated to the high speed side , It is possible to avoid a state in which the operating speed of the preload portion becomes too low (the operating speed at the preload portion can be secured to a certain level or more).

Therefore, in the case where the steplessly driven stepless speed changer is provided in the cut-off harvester, the hydraulic motor of the hydrostatic stepless speed changer is configured to be shiftable, so that the running speed of the gas can be made slower while avoiding the reduction of the driving force The running performance of the cutting harvester could be improved.

In addition, when the running speed of the base and the running speed of the preload are tuned, it is possible to avoid a state in which the operating speed of the preload is too low even if the running speed of the base is sufficiently low Can be ensured at a predetermined level or more), and the cutting performance can be improved in a state where the cropping of the crop reaches a severe part in the cutting work in agricultural land.

Still further, in another solution means, a hydrostatic type continuously variable transmission device to which the power of the engine is transmitted, and the hydrostatic type stepless transmission device is constituted by a hydraulic pump at the upper side of the electric motor and a hydraulic motor at the lower side of the electric motor. A transmission is provided below the hydraulic motor of the hydrostatic stepless speed change unit. The power of the transmission is branched in parallel to the traveling vehicle and the shearing transmission system so that the power of the traveling vehicle is transmitted to the traveling device. The power of the cutting power transmission system is configured to be transmitted to the cutting section, and the cutting transmission system is provided with the cutting transmission.

The operation of the transmission to the low speed side is to operate the power of the hydraulic motor of the hydrostatic type stepless transmission to the low speed side in the structure in which the transmission is provided below the hydraulic motor of the hydrostatic stepless speed change device, If the hydraulic pump of the hydrostatic stepless speed changer is secured to the low speed side, a low speed power having a sufficient driving force (torque) is transmitted from the transmission to the lower side of the transmission.

According to the above configuration, the power of the engine is transmitted to the traveling device through the hydraulic pump, the hydraulic motor, the transmission, and the traveling electric motor of the hydrostatic stepless transmission, and the transmission is capable of being shifted.

Accordingly, when the speed change device is operated to the low speed side in a state in which the discharge amount of the hydraulic pump of the hydrostatic type stepless transmission is ensured, low speed power having sufficient driving force (torque) is transmitted to the traveling device, The driving speed of the low-speed gas can be obtained without the lack of the driving force (torque) in the farmland.

In addition, the power of the transmission is branched in parallel to the running vehicle and the shearing motor, so that the power of the running vehicle is transmitted to the traveling device, and the power of the shearing motor is transmitted to the cutter.

Thus, when the transmission is operated, the shifted power from the transmission is transmitted to the traveling device and the cut-off portion in parallel, so that the traveling speed of the base body and the operating speed of the preload portion are tuned as in Patent Document 1.

It is necessary to make the running speed of the gas sufficiently low when the crop of the crop reaches the severe part in the cutting work in the agricultural land.

As a result, if the speeding device is operated to the low speed side and the traveling speed of the gas is sufficiently slowed down, the operating speed of the preloading portion becomes sufficiently low (the operating speed of the preloading portion becomes too low) (In the case of the mounting part, stable cutting can not be performed unless an operating speed higher than a predetermined level is secured).

On the other hand, according to the above feature of the present invention, since the cut-off transfer system is provided with the cut-off speed shifting device, when the speed changing device is operated to the low speed side to sufficiently lower the running speed of the gas, It is possible to avoid a state in which the operating speed of the mounting becomes too low (the operating speed at the mounting portion can be secured to a certain level or more).

Therefore, in the case where the steplessly driven stepless speed changer is provided in the cut-off harvester, the transmission provided below the hydraulically driven motor of the hydrostatic stepless speed change device is configured to be shiftable so that the driving force (torque) The running speed can be lowered, and the running performance of the cut-off harvester can be improved.

In addition, when the running speed of the base and the running speed of the preload are tuned, it is possible to avoid a state in which the operating speed of the preload is too low even if the running speed of the base is sufficiently low Can be ensured at a predetermined level or more), and the cutting performance can be improved in a state where the cropping of the crop reaches a severe part in the cutting work in agricultural land.

Other features and advantages of the present invention will be apparent from the following description with reference to the accompanying drawings.

1 is an overall side view of a combine according to a first embodiment of the present invention;
2 is a schematic view showing a power transmission system of a combine.
3 is a circuit diagram showing a hydraulic operation circuit of the hydrostatic stepless speed change unit.
4 is a plan view showing a steering panel portion in an operation section;
5 is a block diagram showing a control system of the hydrostatic stepless speed change device.
6 is a block diagram showing a control system of an hydrostatic stepless speed change type transmission according to another embodiment 1 of the first embodiment;
7 is an overall side view of a combine according to a second embodiment of the present invention;
8 is a longitudinal front view of the mission case;
9 is a diagram showing the hydraulic circuit structure of the hydraulic unit.
10 is a view showing a relationship between a shift lever, a travel shift switch, a cut-off shift switch, a steering lever, a turn mode switch, a hydrostatic stepless speed change device, an operation motor, and an oil pressure unit.
11 is a view showing a hydraulic circuit structure of a hydrostatic stepless speed changer.
12 is a view showing a traveling state, a standard cutting state, and a low-speed cutting state.
13 is a longitudinal side view showing an operation structure of the cut-off transmission and the cut-off transmission.
14 is a plan view showing an operation structure of the cut-and-machining transmission.
15 is an overall side view of a combine according to a third embodiment of the present invention;
16 is a longitudinal front view of the mission case;
17 is a view showing a hydraulic circuit structure of the hydraulic unit;
18 is a diagram showing the relationship between the shift lever, the steering lever, the turning mode switch, the hydraulic unit, the operating cylinder, and the pressure control valve.
19 is a diagram showing a hydraulic circuit structure of a hydrostatic stepless speed changer.
FIG. 20 is a view showing a traveling state, a standard cutting state, and a low-speed cutting state in another form (2) of the third embodiment. FIG.
21 is a view showing the relationship between the position of the swash plate of the hydraulic motor of the hydrostatic stepless speed change device and the pressure of the oil chamber of the operating cylinder in another mode (3) of the third embodiment.
22 is a longitudinal front elevational view in the vicinity of a hydrostatic stepless speed changer and a speed shift device according to another embodiment (4) of the third embodiment;
23 is an overall side view of the combine according to the fourth embodiment of the present invention.
24 is a plan view of the operation section;
Fig. 25 is a view showing a linkage state of an operation lever, a lift switch, a setting dial, and a hydraulic cylinder; Fig.
26 is a view showing a flow of operation of the operation lever and the elevation switch in a state in which the setting dial is operated to the OFF position;
Fig. 27 is a view showing a flow of operation of the operation lever and the elevation switch in a state in which the setting dial is operated at the first to sixth falling limits; Fig.
28 is a view showing an operation lever in a state in which the setting dial is operated to the OFF position and an elevating state of the preliminary mounting portion by the elevating switch;
Fig. 29 is a view showing the elevation state of the preliminary mounting portion by the operation lever and the elevation switch in a state in which the setting dial is operated at the first to sixth falling limits; Fig.
30 is a plan view of an operating lever according to another embodiment 1 of the fourth embodiment;

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described with reference to the drawings.

In the following description, unless otherwise specified, the direction in which the traveling gas of the combine advances and retreats is referred to as the forward and backward direction, the horizontal direction orthogonal to the forward and backward direction is referred to as the left-right direction, and the direction perpendicular to the forward- Direction.

[First Embodiment]

First, the first embodiment will be described with reference to Figs. 1 to 6. Fig.

[Overall composition of combine]

Figure 1 shows the overall side of a combine (more specifically, a culm head charging type combine-harvester). The combine is provided with a pair of left and right crawler type traveling devices 11 at the lower part of the base frame 10 and is provided with a cruising operation section 2 having a cockpit 20, And a preload portion 3 is provided on the front portion of the base frame 10 of the base 1. [

The left and right rear portions of the base frame 10 are mounted with the threshing apparatus 12 and the grain keeping apparatus 13 is mounted on the right rear portion of the base frame 10, An engine 14 is provided at a front portion of the engine 14, and the operation portion 2 is disposed above the engine 14.

The preloading section 3 is connected to a support frame (not shown) provided so as to be rotatable around the axis X in the transverse direction of the body, standing upright from the body frame 10, And is vertically swingable through a lift cylinder 15 provided between the base frame 10 and the base frame 10. That is, when the lift cylinder 15 is pivoted up and down with respect to the base frame 10, the lower portion of the raising device 31 is lowered to the lower working state And the raising device (31) are lifted and lowered from the ground to a rising non-working state.

This combine harvests the curved grains such as rice and barley. When the preliminary loading section 3 is driven in a descending operation state and the base body is frequently driven, the preliminary loading section 3 is raised by the raising device 31 And is fed to a barrican-type cutting device 32 to be cut, and the cut slices are transported by the transport device 33 in the backward direction of the substrate and supplied to the starting end of the threshing feed chain 12a of the threshing device 12. The threshing device 12 carries out the threshing process by feeding the bottom end of the cut-off gaps to the back side of the machine by the threshing feed chain 12a while feeding the end of the thread to the threshing chamber (not shown). The grain holding device 13 recovers and stores the threshing lips from the threshing device 12. [

[Power transmission system]

The driving force of the engine 14 is transmitted to the left and right traveling devices 11 and 11 as shown in Fig. 2, a traveling driving system for transmitting the driving force to the traveling devices 11 and 11, a threshing driving system for transmitting the driving force to the threshing device 12, To the cut-off driv- ing system to be conveyed.

That is, in the threshing drive system, the power from the output shaft 14a of the engine 14 is transmitted to the threshing device 12 and the graining storage device 13 (not shown) by the belt transmission mechanism 16 having the threshing clutch 16a ) Or the threshing feed chain 12a.

The traveling driving system transmits the driving force of the output shaft 14a of the engine 14 to the input shaft 40 of the hydrostatic stepless speed change device 4 as the peripheral speed device via the transmission belt 9, And to transmit the driving force of the output shaft 44 of the transmission case 4 to the transmission case 5. In the interior of the transmission case 5, the driving force is transmitted to the pair of left and right steering clutches 51 through a gear type speed reduction mechanism (not shown) to reduce the rotation output of the left steering clutch 51, From the left side of the transmission case 5 to the drive sprocket 11a of the left traveling device 11 and outputs the rotation output of the right side driving clutch 51 from the right side of the transmission case 5, To the drive sprocket (11a) of the traveling device (11).

The cut-off driveline transmits the driving force of the output shaft 12 of the hydrostatic stepless transmission 4 to the working output shaft 52 of the mission case 5 and the driving force of the working output shaft 52 to the pulley- To the input shaft (35) of the preloader (3) through the mechanism (34).

The cutting belt transmission mechanism 34 is provided with an output pulley 52a provided on the working output shaft 52 and an input pulley 35a provided on the input shaft 35 of the pre- And a tension clutch 34a for switching the transmission belt 34b between the tensioned state and the relaxed state to turn ON / OFF the transmission state.

The working output shaft 52 selectively shifts a shift gear (not shown) relative to a known high speed gear (not shown) and a low speed gear (not shown) disposed in the transmission case 5 And a shift transmission 53 for shifting the gears to the high and low gears by engaging with each other. The drive speed is shifted to the high and low gears by the shift operation of the gear shift transmission 53.

[Relationship between hydrostatic stepless speed changer]

The hydrostatic continuously variable transmission 4 constituting the peripheral speed device is of an axial flange type and is of a variable displacement type hydraulic pump 41 and an axial flange type driven by pressure oil from the hydraulic pump 41 And a variable displacement hydraulic motor 42 is also provided. And a charge pump 43 for supplying charge oil to the hydraulic hydraulic circuit for communicating the hydraulic pump 41 and the hydraulic motor 42. [

The hydraulic pump 41 is configured to change the inclined plate angle in conjunction with the operation of the peripheral speed lever (an example of the speed change operation lever) 22 shown in Figs. 4 and 5, And the forward operation region F and the backward operation region R are separately disposed on both sides of the lever 22 and the peripheral speed lever 22 is pushed and pulled in the forward and backward directions, A high-to-low shift by stepless change, a high-to-low shift by stepless change in the reverse side, and a shift operation to a neutral stop position.

The hydraulic motor (42) is constituted by a variable displacement hydraulic motor having a capacity of at least one times the capacity of the hydraulic pump (41). Thus, the hydraulic motor 42 is provided in the running electric system in a state of being arranged in series with the hydraulic pump 41, and has a function as a negative speed shifting device, and the operation of changing the inclined plate angle of the hydraulic motor 42 So that the driving force from the engine 14 is applied to the periphery of the hydraulic pump 41 to be shifted downward to be transmitted to the driving systems of the traveling devices 11, 11 on the left and right sides.

As shown in Fig. 3, the hydraulic motor 42 is structured such that the changing operation of the inclined plate angle is performed by the single acting cylinder 45. Fig. The single acting cylinder 45 is provided with a hydraulic pressure chamber 45a to which pressure oil is supplied to one side of the operation piston 46 and an external opening chamber 46a having a return spring 46a built into the other side of the operation piston 46 45b.

The pressure oil supply path r from the charge pump 43 is connected to the hydraulic pressure chamber 45a and the pressure oil supply path r from the charge pump 43 is connected to the pressure- One proportional pressure reducing valve 47 for controlling the supply pressure is provided.

The proportional pressure reducing valve 47 is configured to supply the supply pressure from the charge pump 43 to the primary pressure and to supply the secondary pressure to the single acting cylinder 45. However, Is set.

3, the proportional pressure reducing valve 47 itself includes a total open position a for supplying the voltage to the secondary side without reducing the primary pressure, a reduced pressure position b for supplying the reduced pressure to the secondary side, As shown in Fig.

The pressure on the secondary side by the proportional pressure reducing valve 47 is greater than the pressure on the return spring 46a at the intermediate position between the tilting torque for returning the neutral position of the hydraulic motor 42 to the neutral position and the elastic range of the single acting cylinder 45 ) And the returning urging force of the return spring 46a is increased so that the operating piston 46 of the single acting cylinder 45 is retracted (contracted) by the standard pressure set to a pressure at which the balance against the return force by the total sum of the returning pressures To the stroke end of the single acting cylinder 45 and the returning urging force of the return spring 46a to a minimum pressure sufficient to extend the working piston 46 of the single acting cylinder 45 up to the stroke end on the extension side It is configured to be able to change the setting.

[Transmission control system]

The speed change control system for controlling the operation of the hydraulic pump 41 and the hydraulic motor 42 of the hydrostatic stepless speed change unit is constructed as follows.

As shown in Fig. 4, the periphery of the operating portion 2 is guided by the guide groove 21A formed on the control panel 21 of the lateral side portion of the cockpit 20, Speed lever 22 is provided. A finger-operated first push button switch 23 (an example of the first operating member) is provided at an upper portion of the grip 22a of the peripheral speed lever 22, and the peripheral speed lever 22 A second push button switch (an example of a second operating port) 24 is provided on the steering panel 21 on the lateral side of the installed position.

4 and 5, the peripheral speed lever 22 is capable of steplessly changing over the neutral position N and the forward region F and the reverse region R, And the operating position of the lever 22 in the periphery is transmitted to the hydrostatic stepless transmission 4 through a mechanical coupling mechanism not shown so that the hydraulic pump 41 of the hydrostatic stepless transmission 4, So that the shifting operation is performed.

The first finger-operated push-button switch 23 provided on the grip 22a of the peripheral speed lever 22 and the second push-button switch 24 provided on the control panel 21 are each pressed The switch is turned ON and the switch is turned OFF by the pushing operation again.

The operation signals of the first and second pushbutton switches 23 and 24 are input to the shift control device 25 constituted by a microcomputer and the operation of the hydraulic motor 42 is controlled by the shift control device 25 The solenoid 47a of the proportional pressure reducing valve 47 to control the operation of the single-acting cylinder 45 to operate the hydraulic motor 42 in a shifting operation.

That is, the finger-operated first push button switch 23 provided on the grip 22a of the peripheral speed lever 22 is operated by the first operation for switching the high speed drive state and the medium speed drive state of the hydraulic motor 42 When the first push button switch 23 is turned ON, the shift control device 25 operates the proportional pressure reducing valve 47 to the entire open position (a) The single-acting cylinder 45 is operated to the fully contracted state against the return spring 46a, and the hydraulic pump 41 is operated to the maximum speed state.

When the first push button switch 23 is pushed again to switch it to the OFF state, the shift control device 25 controls the proportional pressure reducing valve 47 to the reduced pressure position b, The sum of the returning urging force of the return spring 46a on the single acting cylinder 45 side and the tilting torque on the neutral returning side of the hydraulic motor 42 itself is outputted to the middle of the single acting cylinder 45 And the secondary pressure is set by decompression so that the position is balanced.

That is, the first push-button switch 23 selectively switches the speed of the hydraulic motor 42 to the high-speed running region suitable for running on the road and the medium-speed running region suitable for the cutting operation of the upright span in agricultural land And a second operating section for operating the second operating section.

The second push button switch 24 provided on the steering panel 21 constitutes a second operating port for switching between a medium speed drive state and a low speed drive state of the hydraulic motor 42, The shift control device 25 operates the proportional pressure reducing valve 47 from the reduced pressure position b to the fully closed state to stop the supply of the pressure oil from the side of the charge pump 43 do. In this state, the single-acting cylinder 45 is operated to the latest state by the urging force of the return spring 46a and the tilting torque to the neutral return side, thereby operating the hydraulic motor 42 to the low speed state.

When the second push button switch 24 is pushed again to switch it to the OFF state, the proportional pressure reducing valve 47 is controlled so that the shift control device 25 operates the proportional pressure reducing valve 47 to the predetermined reduced pressure position (b) The sum of the returning urging force of the return spring 46a on the single acting cylinder 45 side and the tilting torque on the neutral returning side of the hydraulic motor 42 itself is outputted to the single acting cylinder 45, The secondary pressure by the decompression is set so that the balance is balanced at the intermediate position of the pressure difference.

That is, the second push-button switch 24 selectively switches the speed of the hydraulic motor 42 from the medium-speed running region suitable for the cutting operation of the upright span to the agricultural land and the low-speed running region suitable for the cutting operation of the coating span And a second operating member for operating the second operating member.

In the shift control device 25, only when both the first push button switch 23 and the second push button switch 24 operate the hydraulic motor 42 to the medium speed running region, An operation signal is outputted to the solenoid 47a of the proportional pressure reducing valve 47 so as to perform the switching operation to the high speed range side by the push button switch 23 and the second push button switch 24 or the switching operation to the low speed range side The first push button switch 23 and the second push button switch 24 are operated to the high speed area side or the low speed area side, ) And the second push button switch 24 to the high speed range side or the switching operation to the low speed range side is performed, the switching operation signal is outputted to the solenoid 47a of the proportional pressure reducing valve 47 Ha .

Therefore, when either one of the first push button switch 23 and the second push button switch 24 is operated to the high speed area side or the low speed area side, The first push button switch 23 or the second push button switch 24 may be once returned to the neutral state and then operated to the desired high speed area side or the low speed area side.

When the second push button switch 24 is switched to the low speed running region, the shift control device 25 is controlled so that the cut shear transmission 53 in the drive system of the preload portion 3 is shifted to the high speed side, To the high-speed side with respect to the solenoid 47a of the switching valve provided in the cut-off transmission device 53. [

The output signal from the shift control device 25 is supplied to the shift operating cylinder (not shown) of the cut-off speed shifting device 53 so as to switch the shift gear (not shown) And the solenoid 47a of the valve is turned on / off to perform the pressure multiplying operation.

[Another form 1 of the first embodiment]

In the above embodiment, the linkage between the peripheral speed lever 22 and the hydraulic pump 41 is performed by a mechanical linkage mechanism and the linkage between the push button switches 23 and 24 and the hydraulic motor 42 is connected to the proportional pressure reducing valve 47 or the single-acting cylinder 45. However, the present invention is not limited to this configuration, and may be configured as follows.

For example, in the example shown in Fig. 6, the peripheral speed lever 22 can be steplessly changed over the neutral position N, the forward region F and the backward region R, , The operating position of the lever 22 in the periphery is detected by the potentiometer 26 and the detection signal of the operating position is inputted to the transmission control device 25 constituted by a microcomputer.

The peripheral speed motor 27 of the electric type is linked to the swash plate operation shaft (not shown) of the hydraulic pump 41 of the hydrostatic stepless speed change unit 4 so that the hydraulic pump 41 is rotated by this peripheral speed motor 27 And the transmission control device 25 controls the electric motor based on the detection signal of the operating position inputted from the peripheral speed lever 22 so as to perform normal and reverse rotation control of the electric peripheral speed motor 27, 4 by changing the inclined plate angle 1 of the hydraulic pump 41 to change the speed.

A first push button switch 23 is provided on the peripheral speed lever 22 in association with an electric negative speed change motor 28 on a swash plate operation shaft (not shown) of the hydraulic motor 42, The transmission control device 25 outputs a control signal to the electric reduction gear motor 28 by the operation of the second push button switch provided on the side of the hydraulic motor 42 to shift the hydraulic motor 42 .

[Another form 2 of the first embodiment]

The push-button switches 23 and 24 are not limited to the high-speed and medium-speed, or the middle-speed and low-speed switches, as described in the preferred embodiments, And the medium speed and low speed may be constituted by separate push button switches.

[Other aspect 3 of the first embodiment]

The push-button switches 23 and 24 are not limited to the above-described one, but a lever-operated switch may be used for constituting the first and second operation openings.

[Second Embodiment]

Next, a second embodiment will be described with reference to Figs. 7 to 14. Fig.

[One]

7, the preload part 102 is supported so as to be able to move up and down on the front part of the base supported by the crawler type traveling device 101 on the right and left sides, 103, a threshing device 104 is provided on the left side of the rear part of the base body, and a grain tank 105 is provided on the right side of the rear part of the base body, thereby constituting a comb-

The engine 106 is provided below the operation section 103 and the transmission case 107 is provided near the right and left center of the front section of the gas so that the hydrostatic stepless transmission 107 And is connected to the upper portion of the right side of the mission case 108. A main clutch 109 of a tension type configured by a transmission belt and a tension pulley is provided over the input shaft 107a of the hydrostatic stepless speed change unit 107 and the output shaft 106a of the engine 106. [

The output shaft 107b of the hydrostatic stepless speed change unit 107 is inserted into the transmission case 108 and connected to the low speed gear 110 (transmission shaft 112) by a spline structure , And a high-speed gear 111 is fixed to the power transmission shaft 112. The low speed gear 114 and the high speed gear 115 are externally inserted into the output shaft 113 so as to be relatively rotatable relative to each other so that the low speed gears 110 and 114 and the high speed gears 111 and 115 are engaged, And is externally inserted into the output shaft 113 so as to be able to slide and rotate integrally. A tension type clutch 117 made of a transmission belt and a tension pulley is provided over the output shaft 113 and the input shaft 102a of the preload part 102. [

As shown in Figs. 8 and 13, when the shift member 116 is engaged with the engaging portion 114a of the side surface of the low speed gear 114 (low speed position), the output shaft 107b of the hydrostatic stepless speed changer 107 Is transmitted to the preload unit 102 at a low speed through the low speed gears 110, 114 and the shift member 116. The power of the output shaft 107b of the hydrostatic stepless speed changer 107 is transmitted to the high gears 111 and 115 by engaging the shift member 116 with the engaging portion 115a of the side surface of the high gear 115 And the shift member 116 to the preload unit 102 at a high speed. As described above, the shear transmission device 118 (equivalent to the transmission for the cut-off part) which can be shifted in two levels by low gears 110 and 114, the high gears 111 and 115, the shift member 116, And the cut-off transmission device 118 is disposed under the transmission of the hydrostatic stepless speed change device 107.

[2]

Next, the operation structure of the cut-type transmission device 118 will be described.

The operation shaft 180 is rotatably supported around the longitudinal axis P1 in the transmission case 108 and the operation shaft 180 is rotatably supported in the transmission case 108 as shown in Figures 13 and 14. [ And the operating arm 180a fixed to the shift member 116 is coupled to the shift member 116. [ The operating plate 180b is fixed to the operating shaft 180 and the two pins 180c and 180d are fixed to the operating plate 180b on the outside of the transmission case 108. [

13 and 14, a bracket 181 constructed by bending a plate material is fixed to the mission case 108 and two brackets 181 are provided with two receiving portions 181a and 181b, And the pin 180c of the operating shaft 180 is inserted into the cutout 181c. The outer portion 182b of the wire 182 is fixed to the receiving portion 181a of the bracket 181 and the inner portion 182a of the wire 182 is connected to the pin 180c of the operation shaft 180, And the inner 182a of the motor 182 is connected to the operation motor 183 (see Fig. 10).

The operating rod 184 is slidably inserted into the receiving portion 181b of the bracket 181 so that the operating rod 184 is moved to the pin 180d of the operating shaft 180 Respectively. A receiving portion 184a is fixed to the end portion 1 of the operating rod 184 and a spring 185 is provided between the receiving portion 181b of the bracket 181 and the receiving portion 184a of the operating rod 184. [ And the operating rod 184 is urged by the spring 185 to the left side of the plane of Fig. 13 and Fig. The operating shaft 180 is urged by the spring 185 and the operating rod 184 in the clockwise direction in Fig.14 and the shift member 116 is engaged with the meshing portion 114a of the low speed gear 114 Speed position).

The state shown in Figs. 13 and 14 is a state in which the inner 182a of the wire 182 is returned and operated by the operation motor 183 and the shift member 116 is moved by the spring 185 and the operating rod 184, Is engaged with the low gear 114 (low speed position). In this state, the pin 180c of the operation shaft 180 is in contact with one end face of the cutout portion 181c of the bracket 181, and the operation shaft 180 is stopped at the low speed position.

As shown in Fig. 13, one of the engaging portions 114a of the low-speed gear 114 is formed as an upright surface, and the other is formed of an inclined surface. Thereby, the hydraulic pressure of the hydrostatic stepless speed changer 107 (hydraulic pump 107P) as described later, when the shift member 116 is engaged with the engaging portion 114a of the low gear 114 (low speed position) When the power of the forward side F is transmitted from the output shaft 107b of the low gear 114 to the shift member 116, the upright surface of the engaging portion 114a of the low gear 114 is brought into contact with the shift member 116, ).

When the power of the reverse side R is transmitted from the output shaft 107b of the hydrostatic stepless speed changer 107 (hydraulic pump 107P) as will be described later, the shift member 116 is engaged with the engaging portion of the low gear 114 114a are brought into contact with the spring 185 to be separated from the engaging portion 114a of the low speed gear 114 by the shift member 116 so that the power of the reverse side R is transmitted to the preload portion 102 It is not delivered. As described above, the one-way clutch that transmits the power of the forward side F and does not transmit the power of the reverse side R is provided between the shift member 116 and the engaging portion 114a of the low speed gear 114 .

When the inner 182a of the wire 182 is pulled by the operation motor 183 as shown in Figs. 13 and 14, the operation shaft 180 is rotated counterclockwise in Fig. 14 against the spring 185 The shift member 116 is engaged with the engaging portion 115a of the high gear 115 (high-speed position). In this state, the pin 180c of the operation shaft 180 is brought into contact with the other end face of the notch 181c of the bracket 181, and the operation shaft 180 is stopped at the high speed position.

[3]

Next, the structure of the transmission system (linear system) of the mission case 108 will be described.

The transmission gear 119 is inserted into the transmission shaft 120 so as to be relatively rotatably inserted into the transmission shaft 120 so that the transmission gear 119 meshes with the low speed gear 110 and the shift member 121 is in the spline structure And is externally inserted into the power transmission shaft 120 so as to be able to slide and rotate integrally. The transmission gears 122 and 123 are fixed to the transmission shaft 120 and the multi-plate friction type parking brake 124 is provided at the end of the transmission shaft 120.

The shift member 121 normally meshes with the transmission gear 119 so that the power of the output shaft 107b of the hydrostatic stepless speed changer 107 is transmitted to the low speed gear 110 and the transmission gear 119 (Not shown). The right and left traveling device 101 and the hydrostatic stepless transmission 107 are moved to the position of the shift member 121 by moving the shift member 121 away from the transmission gear 119 at the time of traction of the gas due to failure, So that it is possible to pull the gas without receiving the resistance of the hydrostatic stepless speed change device 107. [

As shown in Fig. 8, the transmission gear 125 is fixed to the transmission shaft 126 and the transmission gears 122 and 125 are engaged with each other. The right and left output gears 127 are externally inserted into the transmission shaft 126 so as to be rotatable relative to each other and the right and left engagement portions 128 are provided on the right and left sides of the right and left output gears 127 in a spline structure And is externally inserted into the power transmission shaft 126 so as to be able to slide and rotate integrally. The right and left transmission gears 129 fixed to the right and left axles 129 are engaged with the right and left output gears 127, And the sprocket 101a (see Fig. 7) of the traveling device 101 on the right and left sides are connected to the end of the axle 129. Fig.

A spring 132 is provided between the receiving member 131 fixed to the transmission shaft 126 and the right engaging portion 128 and the transmission gear 125 and the left engaging portion The right and left engagement portions 128 are urged by the springs 132 to the engagement side of the right and left output gears 127. [ The right oil chamber is formed between the right output gear 127 and the right engaging portion 128 and the left oil chamber is formed between the left output gear 127 and the left engaging portion 128 So that the right and left engaging portions 128 can be separated from the right and left output gears 127 against the spring 132 by supplying operating oil to the right and left oil chambers.

The side clutch 133 on the right side of the meshing type is constituted between the right output gear 127 and the right meshing portion 128 and the left side output gear 127 and the left meshing portion And a side clutch 133 on the left side of the engagement type is formed between the gears 128 and 128. [ The left side side engaging portion 128 is engaged with the right side output gear 127 so that the right side side clutch 133 is in the transmitting state and the right side Side clutch 133 is disconnected by separating the output shaft 128 from the output gear 127 on the right (left) side.

8, the power of the output shaft 107b of the hydrostatic stepless speed changer 107 is transmitted to the low speed gear 110, the transmission gear 119, the transmission shaft 120, the transmission gears 122, Right and left output gears 127 and right and left transmission gears 130 and right and left axles 129 to the left and right sides of the left and right output gears 125, 125, the right and left engaging portions 128, And the traveling device 101 on the left side, and the gas flows straight.

[4]

Next, the structure of the electric system (tachometer) of the mission case 108 will be described.

The transmission gear 135 that is inserted into the transmission shaft 134 so as to be rotatable relatively to the transmission shaft 134 is engaged with the gear portion of the outer peripheral portion of the right engagement portion 128, And a complete line clutch 136 is provided between the gears 135. The quick-turn clutch 136 is formed of a frictional multi-plate type and is pressed in a cut-off state, and is supplied with operating oil, thereby being operated to the electric state and the operating oil to be discharged.

The transmission clutch case 137 is externally inserted into the transmission shaft 126 so as to be relatively rotatable relative to the transmission shaft 126 and the transmission gear 138 and the orbiting clutch case 137, which are fixed to the transmission shaft 134, As shown in Fig. The revolving clutch case 137 is configured to be symmetrical in the left and right directions and a right revolving clutch 139 is provided between the revolving clutch case 137 and the right output gear 127, And a left rotating clutch 139 is provided between the output gears 127 on the left side. The right and left rotating clutches 139 are of a friction multi-disc type, and are supplied with operating oil to be operated in the electric state. In this case, the right and left rotating clutches 139 are arranged such that the friction plates are pressed against each other, so that the right and left rotating clutches 139 are brought into a semi-conductive state even when the working oil is discharged.

8, the power of the power transmission shaft 126 is transmitted to the right engaging portion 128, the transmission gear 135, the relief clutch 136, The transmission shaft 137 and the transmission gear 138 in the same direction as the transmission shaft 126 and is transmitted to the orbiting clutch 137 as a lower speed power than the transmission shaft 126. [ When the right clutch 137 or the left clutch 137 is operated in the cut-off state and the right clutch 139 is operated in the power transmission state, The power is transmitted to the right or left output gear 127 at a speed lower than the speed of the transmission shaft 126. [

As shown in Fig. 8, a brake 140 is provided on the left side of the transmission shaft 134. As shown in Fig. The brake 140 is formed of a frictional multi-plate type, and is supplied with operating oil to be operated in the braking state, and the operating oil is discharged to operate in the released state.

8, when the brake 140 is operated in the braking state, the orbiting clutch case 137 is brought into a braking state via the transmission shaft 134 and the transmission gear 138. [ When the right or left side clutch 133 is operated in the cut-off state and the right or left swing clutch 139 is operated in the power transmission state in the braking state of the brake 140, Is in a braking state.

8, the transmission gear 141 is externally inserted into the transmission shaft 134 in a relatively rotatable manner so that the transmission gears 123 and 141 are meshed with each other and the transmission gear 134 is interposed between the transmission shaft 134 and the transmission gear 141 A reverse rotation clutch 142 is provided. The reverse clutch 142 is formed of a friction multi-plate type and is pushed in a cut-off state, and is supplied with operating oil to be operated in a power transmitting state and discharged in a shut-off state.

8, when the reverse rotation clutch 142 is operated to the power transmission state, the power of the transmission shaft 120 is transmitted to the transmission gears 123 and 141, the reverse rotation clutch 142, the transmission shaft 134, And is transmitted to the orbiting clutch case 137 as a power in the opposite direction to the transmission shaft 126 through the transmission gear 138. When the right or left side clutch 133 is operated to be in the cut-off state and the right or left swing clutch 139 is operated in the power transmission state in the transmission state of the reverse rotation clutch 142, Is transmitted to the output gear 127 on the right or left side.

[5]

Next, the structure of the hydraulic circuit of the hydrostatic-type stepless speed-change device 107 will be described.

11, the hydrostatic stepless speed change unit 107 includes a hydraulic pump 107P and a hydraulic motor 107M (corresponding to a transmission for traveling), and a hydraulic pump 107P and a hydraulic motor 107M are connected by a pair of flow paths 107c. The hydraulic pump 107P of the hydrostatic stepless type stepless shift unit 107 is configured to be steplessly changeable to the neutral position N, the forward side F and the reverse side R, The lever 143 and the swash plate of the hydraulic pump 107P of the hydrostatic stepless speed changer 107 are mechanically linked via the linkage link 86 so that the hydraulic pressure of the hydrostatic pressure- The hydraulic pump 107P of the hydrostatic stepless speed change unit 107 is operated to the neutral position N, the forward side F and the reverse side R by operating the swash plate of the hydraulic pump 107P of the transmission 107 do.

The charge pump 144 is connected to the input shaft 107a of the hydrostatic stepless speed change unit 107 and the input shaft 107a of the hydrostatic stepless speed change unit 107 connects the charge pump 144 to the input shaft 107a, And the charge passage 145 extending from the charge pump 144 is connected to the passage 107c of the hydrostatic stepless speed changer 107 and the filter 149 is provided in the charge passage 145 have. The supply passage 147 is connected to the oil tank 146 provided separately from the transmission case 108 and the charge pump 144 and the filter 148 is provided in the supply passage 147. [

As shown in Fig. 11, the hydraulic motor 107M of the hydrostatic stepless speed change unit 107 shifts to a low speed position for a high speed position for traveling, a middle speed position for cutting work, and a low speed position for a clothes cutting job, . An operating cylinder 156 for operating the swash plate of the hydraulic motor 107M of the hydrostatic stepless speed change unit 107 is provided and the oil passage 157 is branched from the charge passage 145, There is provided a control valve 158 for operating the operation cylinder 156 in a stepless operation.

The relief valve 150 is connected to the charge flow path 145 and the relief valve 150 is connected to the case 151 which houses the hydrostatic stepless speed change device 107, as shown in Fig. The oil passage 152 is connected to the case 151 and the oil tank 146 and the oil cooler 153 is provided in the oil passage 152. [ The flow path 154 is formed over the portion between the charge pump 144 and the filter 148 in the supply flow path 147 and the portion between the case 151 and the oil cooler 153 in the flow path 152, And an opening / closing valve 155 is provided in the flow path 154. The open / close valve 155 is pushed to the closed position and is configured to be opened when the pressure of the flow passage 152 reaches a predetermined low pressure.

The hydraulic oil of the oil tank 146 is supplied to the oil passage 107c of the hydrostatic stepless transmission 107 through the filter 148, the supply passage 147, the charge pump 144 and the charge passage 145, And the operating fluid of the charge flow path 145 is suddenly operated to the operating cylinder 156 via the flow path 157 and the control valve 158. The surplus operating fluid flows to the case 151 through the relief valve 150 . The operating oil from the respective parts of the hydrostatic stepless type stepless shift device 107 and the control valve 158 is discharged to the case 151 and the operating oil of the case 151 is discharged through the oil passage 152 and the oil cooler 153 And returns to the oil tank 146. [

11, when the pressure (back pressure) of the oil passage 152 rises and exceeds a predetermined low pressure due to the oil passage resistance of the oil cooler 153 or the like, the open / close valve 155 is operated to the open position, The operating oil of the oil passage 152 is supplied to the supply oil passage 147 so that the pressure in the oil passage 152 and the oil cooler 153 is prevented from rising.

[6]

Next, the operation of the hydraulic motor 107M, the sheathed clutch 17 and the shear transmission (18) of the hydrostatic stepless speed change unit 107 will be described.

10, a shift selector switch 187 (an articulated manipulator) is provided at the lower portion of the lateral surface portion of the grip portion 143a of the shift lever 143 in the grip portion 143a at the upper portion of the shift lever 143, And a shift selector switch 188 (corresponding to an articulated manipulation tool) is provided on the upper portion of the rear surface portion of the grip portion 143a of the shift lever 143. As shown in Fig. The traveling change-speed switch 187 and the cut-off speed-change switch 188 are formed in a push-button type and are urged toward the return side (projecting side) (179).

As shown in Fig. 10, the operation motor 183 and the cut-off clutch 117 are mechanically linked, and the cut-off clutch 117 and the cut-off transmission 118 are operated by one operation motor 183 . Thereby, the state in which the cut-off clutch 117 is operated to the disconnected state and the cut-off transmission 118 is operated to the low-speed position, the cut-off clutch 117 is operated to the power transmission state by the operation motor 183, 118 are in the low speed position, the cut clutch 117 is operated in the power transmission state, and the cut-off transmission 118 is operated in the high speed position.

As shown in Fig. 12, the control device 179 controls the control valve 158 (Fig. 12) in the traveling state, the standard cutting state, and the low-speed cutting state, The operation cylinder 156) and the operation motor 183 are operated as follows.

The traveling running state is a state in which the hydraulic motor 107M of the hydrostatic stepless speed change unit 107 is operated to the high speed position for traveling and the cut clutch 117 is operated to the cutoff state, (Corresponding to operating means for operating the cut-off clutch to the cut-off state when the traveling running condition is set).

The standard cutting state is a state in which the hydraulic motor 107M of the hydrostatic stepless speed change unit 107 is operated to a medium speed position for cutting work and the cut clutch 117 is operated to a power transmitting state, It is in an operated state.

The low-speed cutting state is a state in which the hydraulic motor 107M of the hydrostatic stepless speed change unit 107 is operated to a low speed position for the overlay cutting work where the oversized crop is assumed, the cutting clutch 117 is operated in the rolling state, The device 118 is in a high-speed position.

The control valve 158 (operating cylinder 156) and the operating motor 183 are operated as follows by the control device 179 on the basis of the pressing operation of the traveling speed change switch 187 and the cut-off speed change switch 188 .

As shown in Fig. 12, when the traveling speed change switch 187 is depressed and the standard cut condition is set and the standard cut condition is set, When the operation is pushed, the travel running state is set. Thus, the traveling state and the standard cutting state are alternately set each time the travel shift switch 187 is pressed.

In this case, as shown in Fig. 12, even if the cut-state shifting switch 188 is pressed in the state in which the traveling state is set, the pushing operation is ignored and the traveling state is maintained. When the sorting shift switch 188 is depressed in a state in which the standard cut state is set by pressing the traveling speed change switch 187, a low cut state is set (from the travel running state to the low cut state As a check means for inhibiting the setting state of the display device).

As shown in Fig. 12, in the state that the standard cut condition is set, when the cut cut-off speed switch 188 is pressed, a low cut condition is set. If the cut-off speed change switch 188 is depressed while the low-speed cut-off state is set, the standard cut-off state is set. Each time the cut-off shifting switch 188 is depressed, the standard cut condition and the low cut condition are alternately set.

In this case, as shown in Fig. 12, even if the travel shift switch 187 is pressed in the state in which the low-speed cut state is set, this pressing operation is ignored and the low-speed cut state is maintained. When the coasting shift switch 188 is depressed to set the standard cut state, the travel shift state is set when the travel shift switch 187 is depressed (the coasting state is changed from the low-speed cut state to the travel state As a check means for inhibiting the setting state of the display device).

[7]

Next, the right and left side clutches 133 (right and left engaging portions 128), the right and left circulating clutches 139, the relief clutch 136, the brakes 140, 142 to the hydraulic unit 159 for operating the hydraulic oil.

8 and 9, an oil pressure unit 159 is connected to a lower portion of the left side of the mission case 108. As shown in Fig. The hydraulic pump 160 is connected to the input shaft 107a of the hydrostatic stepless type speed changer 107 and the hydraulic pump 160 is driven by the input shaft 107a of the hydrostatic stepless transmission 107, And the oil line 161 extending from the hydraulic pump 160 is connected to the oil pressure unit 159. [

9, the supply passage 162 is connected to the transmission case 160 through the transmission case 160, the oil cooler 163 is provided in the supply passage 162, A filter 164 is provided at a portion between the hydraulic pump 160 and the oil cooler 163 in the oil cooler 163. The bypass passage 165 is connected between the portion of the supply passage 162 on the side of the mission case 108 and the portion between the oil cooler 163 and the filter 164 in the supply passage 162 So that the flow path resistance of the bypass flow path 165 is also small in the flow path resistance of the oil cooler 163.

9, the lubricating oil stored in the transmission case 108 is divided into the oil cooler 163 and the bypass passage 165 as hydraulic oil, joined together, passed through the filter 164, (Not shown). The operating oil of the hydraulic pump 160 is supplied to the hydraulic unit 159 through the oil line 161 and the hydraulic oil discharged from each part of the oil pressure unit 159 is returned to the mission case 108 as described later.

9, the oil pressure unit 159 includes a priority control valve 167, a left turn control valve 168, a first relief valve 169, an unload valve 170, a second relief valve 169, A pilot control valve 176, a proportional control valve 171, a swing switching control valve 172, and pilot control valves 173 and 174 are provided. The oil passage 161 of the hydraulic pump 160 is connected to the oil pressure unit 159 and the right and left swing control valves 167 and 168 and the first relief valve 169 are connected to the oil passage 166 connected to the oil passage 161 And an unloading valve 170 are connected in parallel.

9, the priority control valve 167 is connected to the right side clutch 133 (the right engaging portion 128) and the right side revolving clutch 139, and the left turn control valve 168 are connected to the left side clutch 133 (left side engaging portion 128) and the left side rotating clutch 139, respectively. The right and left swivel control valves 167 and 168 are electromagnetically operable to be operable with the supply positions 167a and 168a and the discharge positions 167b and 168b and are urged into the discharge positions 167b and 168b. The unloading valve 170 is electromagnetically operable to be operable to the shutoff position 170a and the discharge position 170b and is urged to the shutoff position 170a.

The second relief valve 176 is connected to the oil line 175 branched from the right and left side clutches 133 (right and left engaging portions 128) The proportional control valve 171 and the swing switching control valve 172 are connected in series to each other and the swing switching control valve 172 is connected to the brake solenoid clutch 136, Respectively. The proportional control valve 171 is constituted by an electromagnetic operation type, and pressure control of the operating oil is possible. The swivel switch control valve 172 is configured in a pilot operated manner operable with a grand turn position 172a, a pivot turn position 172b and an extreme spin turn position 172c And is pushed to the full turn position 172a. In this case, the relief pressure of the first relief valve 169 is set to a relatively high value and the relief pressure of the second relief valve 176 is set to a relatively low value.

9, the pilot operated valve 173 is configured to supply the pilot hydraulic fluid branched from the oil passage 175 to the swing switching control valve 172 to be operated to the ground pivot position 172b, and the oil passage 175 The pilot operation valve 174 is configured to supply the pilot operated hydraulic fluid branched from the pilot control valve 172 to the swing switching control valve 172 to operate the swing switching control valve 172 to the extension pivot position 172c. A drain passage (not shown) is formed on the connection surface (mating surface) between the hydraulic unit 159 and the mission case 108 and the rotation control valve 167, the left turn control valve 168, The operating fluid of the valve 169, the unloading valve 170, the second relief valve 176, the proportional control valve 171, the swing switching control valve 172 and the pilot operating valves 173, And returned to the case 108.

The right and left swing control valves 167 and 168, the unloading valve 170, the proportional control valve 171 and the pilot control valves 173 and 174 are described in [8] [9] [10] [11] And is operated by the control device 179 as described above.

[8]

Next, the straight-ahead state by the steering lever 177 will be described.

7 and 10, a steering lever 177 which can be operated to the right and to the left is provided in the operation section 103 and the operation position of the steering lever 177 is inputted to the control device 179 , The steering lever 177 is configured to be operable by the linear position N, the right and left first pivot positions R1 and L1, and the right and left second pivot positions R2 and L2. The turning mode switch 178 is provided in the operation unit 103 and the operating position of the turning mode switch 178 is inputted to the control device 179. The turning mode switch 178 is set to the full turn position, And an extreme pivot position.

8 to 10, when the steering lever 177 is operated to the straight forward position N regardless of the operating position of the turn mode switch 178, the right and left turn control valves 167, Positions 167b and 168b, and the unloading valve 170 is operated to the discharge position 170b. As a result, the hydraulic oil is discharged from the right and left side clutches 133 (right and left meshing portions 128) and right and left swing clutches 139, and the right and left side clutches 133 And the left engaging portion 128) are operated to the power transmission state, and the right and left revolving clutches 139 are operated in the inverted state. The proportional control valve 171 operates the disengaged brake and reverse clutches 136 and 142 to the disconnected state and the brake 140 to the disengaged state.

The power of the output shaft 107b of the hydrostatic stepless speed changer 107 is transmitted to the low gear 110, the transmission gear 119, the transmission shaft 120, the transmission gear (not shown) Right and left output gears 127 and right and left transmission gears 130 and right and left axles 129 are connected to the right and left output gears 127, 122, 125, the transmission shaft 126, the right and left engaging portions 128, To the traveling device 101 on the right and left sides, and the gas flows straight.

[9]

Next, the state of the complete turn by the steering lever 177 will be described.

8 to 10, when the turn mode switch 178 is operated to the complete turn position, the pilot control valves 173 and 174 operate the turn control valve 172 to the complete turn position 172a do. Thereby, when the steering lever 177 is operated to the right first pivotal position R1, the priority control valve 167 is operated to the supply position 167a and the unloading valve 170 is operated to the cutoff position 170a The operating oil is supplied to the right side clutch 133 (right meshing portion 128) and the right side swing clutch 139 and the right side clutch 133 (right meshing portion 128) And the right side turning clutch 139 is operated in the electric state.

The power of the left side clutch 133 (the left engaging portion 128) is transmitted to the left output gear 127 and the left side clutch 137 (left engaging portion 128) because the left side turning clutch 139 is in a half- Is transmitted from the revolving clutch 139 to the right side output gear 127 through the right side rotating clutch 139 and a power slightly lower in speed than the power transmission shaft 126 and in the same direction as the power transmission shaft 126 is transmitted to the right output gear 127, (127). As a result, the gas gently changes direction to the right.

8 to 10, when the steering lever 177 is operated to the right first pivotal position R1, the priority control valve 167 is operated to the supply position 167a as described above, And the operating oil is supplied to the relief clutch 136 via the proportional control valve 171 and the swing switching control valve 172 (relief turn position 172a) And when the steering lever 177 is operated from the right first pivotal position R1 to the right second pivotal position R2, the operating pressure of the relieving clutch 136 by the proportional control valve 171) Up operation is performed.

As shown in Figs. 8 to 10, when the operating pressure of the relief clutch 136 is raised by the proportional control valve 171 based on the operating position of the steering lever 177, The power of the power transmission gear 133 is transmitted to the right engaging portion 128, the transmission gear 135, the tightening clutch 136, the transmission shaft 134, the transmission gear 138, the orbiting clutch case 137, And is transmitted to the right output gear 127 as a lower speed power than the power transmission shaft 126. [

In this case, as shown in Fig. 8, the power from the left side clutch 133 (the left engaging portion 128) and the power from the relief clutch 136 are transmitted to the right output gear 127 at the same time The power from the left side clutch 133 (the left engaging portion 128) is transmitted to the left side clutch 136 via the left side clutch 136 while the operating pressure of the complete brake clutch 136 is low, The right side output gear 127 is driven by the power from the side clutch 133 (the left engaging portion 128). As a result, when the operating pressure of the fastening line clutch 136 is low, the gas gently changes direction to the right.

Next, when the operating position of the steering lever 177 approaches the right second pivotal position R2 and the operating pressure of the relief clutch 136 reaches a high pressure, as shown in Fig. 8, The power is transmitted from the left side clutch 133 (the left engaging portion 128) and the right side output gear 127 is driven by the power from the complete line clutch 136. [ In this state, the right side output gear 127 is driven by the power from the left side clutch 133 (left side engaging portion 128) The output gear 127 of the right side is driven at a low speed and the base body is wound to the right side.

8 to 10, when the steering lever 177 is operated to the left first pivotal position L1, the left turn control valve 168 is operated to the feed position 168a and the unloading valve 170 is operated, The operating oil is supplied to the left side clutch 133 (the left engaging portion 128) and the left side rotating clutch 139 to operate the left side clutch 133 The engaging portion 128) is operated to the disconnected state, and the left swing clutch 139 is operated to the electric state. At the same time, the above operation is performed, and the gas gently changes direction to the left. When the steering lever 177 is operated from the left first pivotal position L1 to the left second pivotal position L2, the above-described operation is performed, and the gas turns to the left side.

[10]

Next, the state of the landing by the steering lever 177 will be described.

8 to 10, when the turn mode switch 178 is operated to the stop position, the pilot control valves 173 and 174 operate the swing switching control valve 172 to the stop position 172b .

Thereby, when the steering lever 177 is operated to the right first pivotal position R1, the priority control valve 167 is operated to the supply position 167a and the undo valve 170 is operated to the shutoff position 170a The operating fluid is supplied to the right side clutch 133 (right meshing portion 128) and the right side swing clutch 139 so that the right side clutch 133 (right meshing portion 128) And the right turning clutch 139 is operated in the electric state. In this case, since the left swing clutch 139 is in an inverted state, the vehicle gently changes its direction to the right as described in [9].

8 to 10, when the steering lever 177 is operated to the right first pivotal position R1, the priority control valve 167 is operated to the supply position 167a as described above, The hydraulic oil is started to be supplied to the brake 140 via the proportional control valve 171 and the swing switching control valve 172 (the pivot position 172b) And the operating pressure of the brake 140 is stepped up by the proportional control valve 171 as the steering lever 177 is operated from the right first pivot position R1 to the right second pivot position R2.

8 to 10, when the operating pressure of the brake 140 is stepped up by the proportional control valve 171 based on the operating position of the steering lever 177, the driving shafts 134, The braking force is applied to the right output gear 127 through the transmission gear 138, the swing clutch case 137 and the right swing clutch 139.

In this case, as shown in Fig. 8, the state in which the power from the left side clutch 133 (the left engaging portion 128) and the braking force of the brake 140 are simultaneously transmitted to the right output gear 127 The power from the left side clutch 133 (the left engaging portion 128) overcomes the braking force of the brake 140 when the operating pressure of the brake 140 is in the low pressure range and the left side clutch 133 The right output gear 127 is driven by the power from the [left engaging portion 128]. As a result, when the operating pressure of the brake 140 is in the low pressure range, the gas gently changes direction to the right.

Next, when the operating position of the steering lever 177 approaches the right second pivotal position R2 and the operating pressure of the brake 140 becomes high, as shown in Fig. 8, the braking force of the brake 140 becomes The power from the side clutch 133 (the left engaging portion 128) is applied, the braking force of the brake 140 causes the right output gear 127 to be in the braking state, and the vehicle is pivoted to the right.

8 to 10, when the steering lever 177 is operated to the left first pivotal position L1, the left turn control valve 168 is operated to the feed position 168a and the unloading valve 170 is operated, The operating oil is supplied to the left side clutch 133 (left side engaging portion 128) and the left side rotating clutch 139 to operate the left side clutch 133 (left side engaging portion (128) is operated in the cut-off state, and the left-hand rotating clutch 139 is operated in the electric state. At the same time, the above operation is performed, and the gas gently changes direction to the left. When the steering lever 177 is operated from the left first pivotal position L1 to the left second pivotal position L2, the above-described operation is performed, and the gas is pivoted to the left.

[11]

Next, the state of the pickup lever 177 in the pick-up position will be described.

8 to 10, when the swing mode switch 178 is operated to the full-stroke swing position, the swing switching control valve 172 is depressed by the pilot control valves 173 and 174 to the swing pivot position 172c .

Thereby, when the steering lever 177 is operated to the right first pivotal position R1, the priority control valve 167 is operated to the supply position 167a and the unloading valve 170 is operated to the shutoff position 170a The operating oil is supplied to the right side clutch 133 (right meshing portion 128) and the right side swing clutch 139 and the right side clutch 133 (right meshing portion 128) And the right turning clutch 139 is operated in the electric state. In this case, since the left swing clutch 139 is in an inverted state, the vehicle gently changes its direction to the right as described in [9].

8 to 10, when the steering lever 177 is operated to the right first pivotal position R1, the priority control valve 167 is operated to the supply position 167a as described above, The hydraulic oil is supplied to the reverse rotation clutch 142 through the proportional control valve 171 and the swing switching control valve 172 (the extension position of the swing pivot position 172c) And the operating pressure of the reverse clutch 142 is increased by the proportional control valve 171 as the steering lever 177 is operated from the right first pivot position R1 to the right second pivot position R2, .

As shown in Figs. 8 to 10, as the operating pressure of the reverse rotation clutch 142 is stepped up by the proportional control valve 171 based on the operating position of the steering lever 177, Is transmitted through the transmission gears 123 and 141, the reverse rotation clutch 142, the transmission shaft 134, the transmission gear 138, the swing clutch case 137 and the right swing clutch 139 126 to the right output gear 127 as power in the opposite direction.

In this case, the power from the left side clutch 133 (the left engaging portion 128) and the power from the reverse rotation clutch 142 are simultaneously transmitted to the right output gear 127 The power from the left side clutch 133 (the left engaging portion 128) receives the power from the reverse rotation clutch 142 when the operating pressure of the reverse rotation clutch 142 is in the low pressure range The right output gear 127 is driven by the power from the left side clutch 133 (left engaging portion 128). Thus, when the operating pressure of the reverse rotation clutch 142 is in the low pressure range, the gas gently changes direction to the right.

Next, when the operating position of the steering lever 177 approaches the right second pivotal position R2 and the operating pressure of the reverse rotation clutch 142 becomes high, as shown in Fig. 8, The power is supplied from the left side clutch 133 (the left engaging portion 128L), and the right output gear 127 is driven by the power from the reverse rotation clutch 142. In this state, the output gear 127 on the right side is driven in the reverse direction with respect to the left output gear 127, and the base body is pivoted to the right.

8 to 10, when the steering lever 177 is operated to the left first pivotal position L1, the left turn control valve 168 is operated to the feed position 168a and the unloading valve 170 is operated, The operating oil is supplied to the left side clutch 133 (the left engaging portion 128) and the left side rotating clutch 139 to operate the left side clutch 133 (left side engaging portion (128) is operated in the cut-off state, and the left-hand rotating clutch 139 is operated in the electric state. At the same time, the above operation is performed, and the gas gently changes direction to the left. When the steering lever 177 is operated from the left first pivotal position L1 to the left second pivotal position L2, the above-described operation is performed, and the base body is pivoted to the left.

[Other aspect 1 of the second embodiment]

8, an auxiliary transmission (not shown) (corresponding to a traveling transmission) is provided below the transmission shaft 112 separately from the hydrostatic stepless transmission 107, The auxiliary speed change device may be configured to be capable of being operated at a high speed position for traveling, a medium speed position for cutting work, and a low speed position for a clothes cutting work where the heavy clothes are taken.

In such a configuration, the auxiliary transmission is operated to the high speed position in the traveling state, the auxiliary transmission is operated to the intermediate speed position in the standard cutting state, and the auxiliary transmission is operated to the low speed position in the low speed cutting state.

[Another form 2 of the second embodiment]

The hydraulic pump 107P of the hydrostatic stepless speed changer 107 is operated to the high speed position and the hydraulic pump 107P of the hydrostatic stepless transmission 107 is switched to the intermediate speed position And the hydraulic pump 107P of the hydrostatic stepless speed change unit 107 is operated to the low speed position in the low speed cutting state.

[Another form 3 of the second embodiment]

In the state in which the standard cutting state is set and the cutting clutch 117 is not automatically configured to be operated in the transmission state by the operation of the traveling speed change switch 187 being pressed, The cut-off clutch 117 may be configured so as to be operable in a power transmission state or a cut-off state by an artificial operation opening (for example, a cutoff clutch lever) different from that of the traveling changeover switch 187 and the cut- In this case, in the state where the cut-off clutch 117 is operated to the power transmission state by the other artificial operation tool in the standard cut state, when the travel shift state is set by the operation of the travel shift switch 187, It is operated in the cutoff state.

[Other aspect 4 of the second embodiment]

The traveling speed change switch 187 and the cut-off speed change switch 188 are abolished and the traveling state, the standard cutting state and the low-speed cutting state are set by a single shift switch (corresponding to an artificial operation opening) .

In this case, when the shift running state is set from the low-speed cutting state by the shift switch, the standard cutting state is set from the low-speed cutting state, and then the traveling state is set from the standard cutting state. When the low-speed cutting state is set from the traveling state by the shift switch, the standard cutting state is set from the traveling running state, and then the low-speed cutting state is always set from the standard cutting state.

The traveling speed change switch 187 and the cut-off speed change switch 188 or the speed change switch is provided not on the grip portion 143a of the shift lever 143 but on the steering panel on the front side portion of the operation portion 103 or the side panel on the lateral side portion Maybe.

[Another aspect 5 of the second embodiment]

The above-described cut-off transmission 118 may be configured to be capable of continuously-variable shifting (for example, a hydrostatic stepless transmission or a belt continuously variable transmission).

In this configuration, the cut-type transmission 118 is configured to be capable of continuously variable transmission at an appropriate shift position in the vicinity of the low-speed position while the cut-type transmission 118 is operated to the low-speed position in the standard cut state. Variable transmission device 118 is configured to be capable of continuously variable transmission at an appropriate shift position in the vicinity of the high-speed position in a state in which the cut-type speed change device 118 is operated to the high speed position in the low-speed cut state.

[Third embodiment]

Next, a third embodiment will be described with reference to Figs. 15 to 22. Fig.

[One]

As shown in Fig. 15, a traveling device 202 is supported so as to be able to move up and down on a front portion of a base supported by right and left crawler type traveling devices 201, 203 is provided on the left side of the rear portion of the base body and a grain tank 205 is provided on the right side of the rear portion of the base body to constitute a comb shape of the cutting type harvesting machine as an example of the cutting and harvesting machine.

16, the engine 206 is provided below the operation unit 203, the transmission case 208 is provided near the right and left center of the front portion of the vehicle, and the hydrostatic stepless transmission 207 A belt transmission mechanism 209 having a tension clutch function is connected to the input shaft 207a of the hydrostatic stepless speed changer 207 and the output shaft 206a of the engine 206, Respectively.

The output shaft 207b of the hydrostatic stepless speed changer 207 is inserted into the transmission case 208 and connected to the low speed gear 210 (the transmission shaft 212) by a spline structure , And a high-speed gear 211 is fixed to the transmission shaft 212. The low speed gear 214 and the high speed gear 215 are externally inserted into the output shaft 213 in such a manner that the low speed gear 214 and the high speed gear 215 are relatively rotatably inserted into the low speed gears 210 and 214 and the high speed gears 211 and 215, And is externally inserted into the output shaft 213 so as to be capable of sliding and integrally rotating. A belt transmission mechanism 217 having a tension clutch function is connected to the output shaft 213 and the input shaft 202a of the traveling device 202. [

The power of the output shaft 207b of the hydrostatic stepless speed changer 207 is transmitted to the low gears 210 and 214 by engaging the shift member 216 with the low gear 214 (low speed position) The output shaft 207b of the hydrostatic stepless speed changer 207 is shifted to the high speed gear 215 by being transmitted to the traveling device 202 at a low speed through the shift member 216 and by engaging the shift member 216 with the high speed gear 215 Is transmitted to the traveling device 202 at a high speed through the high speed gears 211, 215 and the shift member 216. As described above, the low speed gears 210 and 214, the high speed gears 211 and 215, the shift member 216 and the like constitute a speed change transmission device 218 capable of shifting in two levels.

[2]

Next, the structure of the electric system (linear system) of the mission case 208 will be described.

The transmission gear 219 is inserted into the transmission shaft 220 so as to be relatively rotatably inserted into the transmission shaft 220 so that the transmission gear 219 meshes with the low speed gear 210 and the shift member 221 is engaged with the spline structure And is externally inserted into the transmission shaft 220 so as to be able to slide and rotate integrally. The transmission gears 222 and 223 are fixed to the transmission shaft 220 and the multi-plate friction type parking brake 224 is provided at the end of the transmission shaft 220.

The shift member 221 normally meshes with the transmission gear 219 so that the power of the output shaft 207b of the hydrostatic stepless speed changer 207 is transmitted to the low gear 210 and the transmission gear 219 to the transmission shaft 220 through the transmission shaft. The right and left traveling devices 201 and the hydrostatic stepless transmission 207 are moved to the position of the shift member 221 by moving the shift member 221 away from the transmission gear 219 at the time of traction of the gas due to failure, And it is possible to pull the gas without receiving the resistance of the hydrostatic stepless speed change device 207. [

16, the transmission gear 225 is fixed to the transmission shaft 226 and the transmission gears 222 and 225 are engaged with each other. The right and left output gears 227 are externally inserted into the transmission shaft 226 so as to be rotatable relative to each other and the right and left meshing portions 228 are provided on the right and left sides of the right and left output gears 227, And is externally inserted into the power transmission shaft 226 so as to be able to slide and rotate integrally. Right and left transmission shafts 229 and right and left transmission gears 230 fixed to the right and left axles 229 are engaged with right and left output gears 227, The sprocket 201a (see Fig. 15) of the traveling device 201 on the right and left sides is connected to the end portion of the axle 229. Fig.

16, a spring 32 is provided between the housing member 31 fixed to the transmission shaft 226 and the right engaging portion 228, and the transmission gear 225 and the left engaging portion The right and left engagement portions 228 are urged by the springs 32 toward the engaging side of the right and left output gears 227. As a result, The right side oil chamber is formed between the right output gear 227 and the right side engagement portion 228 and the left side oil chamber is formed between the left side output gear 227 and the left side engagement portion 228, And the right and left engagement portions 228 can be separated from the right and left output gears 227 against the spring 32 by supplying the operating oil to the left oil chamber.

The left side output clutch 223 and the left side output gear 227 constitute the right side side clutch 233 of the engaging type between the right side output gear 227 and the right side engaging portion 228, A side clutch 233 on the left side of the engaging type is formed between the clutches 228 and 228. [ The left side side engaging portion 228 is engaged with the right side output gear 227 so that the right side side clutch 233 is in the transmitting state and the right side The left clutch 223 is separated from the right side output gear 227 and the right side clutch 233 is shut off.

16, the power of the output shaft 207b of the hydrostatic stepless speed changer 207 is transmitted to the low speed gear 210, the transmission gear 219, the transmission shaft 220, the transmission gears 222, The right and left output gears 227 and the right and left transmission gears 230 and the right and left axles 229 to the left and right sides of the right and left axles 226, 225 and 226, the right and left meshing portions 228, And the traveling device 201 on the left side, and the gas goes straight.

[3]

Next, a description will be given of the structure of the electric system (tilting system) of the mission case 208. Fig.

The transmission gear 235 that is inserted into the transmission shaft 234 so as to be relatively rotatable is engaged with the gear portion of the outer peripheral portion of the right engaging portion 228 and the transmission gear 234 And a complete line clutch 236 is provided between the transmission gears 235. The striking wheel clutch 236 is formed of a friction multi-disc type and is pressed in a cut-off state, and is supplied with operating oil to be operated in the electric state, and the operating oil is discharged to operate in the cut-off state.

The transmission clutch case 237 is inserted into the transmission shaft 226 so as to be relatively rotatable relative to the transmission shaft 226 and the transmission gear 238 and the orbiting clutch case 237 fixed to the transmission shaft 234, As shown in Fig. The revolving clutch case 237 is configured to be bilaterally symmetrical and includes a revolving clutch case 239 disposed between the revolving clutch case 237 and the right output gear 227, And a left rotating clutch 239 is provided between the output gears 227. [ The right and left revolving clutches 239 are of a friction multi-disc type, and are supplied with operating oil to be operated in the electric state. In this case, the right clutch 239 and the left clutch 239 are arranged so that the friction plates are pressed against each other, so that the right and left clutches 239 are brought into a semi-conductive state even when the operating oil is discharged.

16, the power of the power transmission shaft 226 is transmitted to the right engaging portion 228, the transmission gear 235, the relief clutch 236, The electric power is transmitted to the orbiting clutch case 237 through the transmission shaft 234 and the transmission gear 238 in the same direction as the transmission shaft 226 and at a lower speed than the transmission shaft 226. When the right clutch 233 is operated in the cut-off state and the right clutch 239 is operated in the power transmission state in the transmission state of the coasting clutch 236, the same as the transmission shaft 226 Direction and a power of lower speed than that of the transmission shaft 226 is transmitted to the right or left output gear 227.

As shown in FIG. 16, a brake 240 is provided on the left side of the transmission shaft 234. The brake 240 is formed of a frictional multi-plate type, and is supplied with operating oil to be operated in the braking state, and the operating oil is discharged to operate in the released state.

16, when the brake 240 is operated to the braking state, the orbiting clutch case 237 is brought into a braking state via the transmission shaft 234 and the transmission gear 238. [ When the right or left side clutch 233 is operated in the cut-off state and the right or left clutch 239 is operated in the power transmission state in the braking state of the brake 240, the right or left output gear 227 Is in a braking state.

16, the transmission gear 241 is inserted into the transmission shaft 234 so that the transmission gear 241 can be relatively rotatably inserted into the transmission gear 233 and the transmission gears 223, 241 are engaged with each other, and the transmission gear 234 is interposed between the transmission gear 234 and the transmission gear 241 A reverse rotation clutch 242 is provided. The reverse rotation clutch 242 is formed of a friction multi-plate type and is pressed in a cut-off state, and is supplied with operating oil to be operated in the electric state, and the operating oil is discharged to operate in the cut-off state.

16, when the reverse rotation clutch 242 is operated in the power transmission state, the power of the transmission shaft 220 is transmitted to the transmission gears 223 and 241, the reverse rotation clutch 242, the transmission shaft 234 And is transmitted to the orbiting clutch case 237 as a power in the direction opposite to the transmission shaft 226 via the transmission gear 238. When the right or left side clutch 233 is operated in the cut-off state and the right or left clutch 239 is operated in the power transmission state in the transmission state of the reverse rotation clutch 242, Is transmitted to the output gear 227 on the right or left side.

[4]

Next, the hydraulic circuit structure of the hydrostatic stepless speed change device 207 will be described.

19, the hydrostatic stepless type continuously variable transmission 207 is provided with an axial pump type hydraulic pump 207P and a hydraulic motor 207M, and a hydraulic pump 207P and a hydraulic motor 207M And is connected to a flow path 207c. The charge pump 244 is connected to the input shaft 207a of the hydrostatic stepless speed change device 207 and the charge pump 244 is driven by the input shaft 207a of the hydrostatic stepless speed change device 207. [

The bypass flow passage 283 is connected to the flow passage 207c of the hydrostatic stepless speed change device 207 and the charge flow passage 245 extended from the charge pump 244 is connected to the bypass flow passage 283, And a filter 49 is provided in the charge flow path 245. [ A check valve 284 and a throttle portion 285 and a relief valve 286 are provided between a portion of the bypass passage 283 to which the charge passage 245 is connected and a passage 207c of the hydrostatic stepless speed changer 207, And the relief pressure of the relief valve 286 is set to the maximum allowable pressure of the hydrostatic stepless speed changer 207 as a whole. A supply channel 247 is connected to the oil tank 246 provided separately from the transmission case 208 and the charge pump 244 and a filter 248 is provided in the supply channel 247.

The relief valve 250 is connected to the charge flow path 245 and the relief valve 250 is connected to the case 251 that houses the hydrostatic stepless speed change device 207 as shown in Fig. A flow path 252 is connected to the case 251 and the oil tank 246 and an oil cooler 253 is provided in the flow path 252. [ A flow path 254 is formed between a portion between the charge pump 244 and the filter 248 in the supply flow path 247 and a portion between the case 251 and the oil cooler 253 in the flow path 252. [ And an opening / closing valve 255 is provided in the flow path 254. The opening / The open / close valve 255 is pushed to the closed position and is configured to be opened when the pressure of the flow path 252 reaches a predetermined low pressure.

The hydraulic oil of the oil tank 246 is supplied to the oil passage 207c of the hydrostatic stepless speed changer 207 through the filter 248, the supply passage 247, the charge pump 244 and the charge passage 245, And the surplus hydraulic fluid is discharged to the case 251 through the relief valve 250. [ The hydraulic oil from each part of the hydrostatic stepless speed change device 207 is discharged to the case 251 and the operating oil of the case 251 passes through the oil passage 252 and the oil cooler 253 to the oil tank 246 Is returned.

19, when the pressure (back pressure) of the oil passage 252 rises and exceeds a predetermined low pressure due to the oil passage resistance of the oil cooler 253 or the like, the open / close valve 255 is operated to the open position, The operating fluid of the oil passage 252 is supplied to the supply passage 247 to suppress the increase of the pressure in the oil passage 252 and the oil cooler 253.

[5]

Next, the operation structure of the hydrostatic stepless speed change device 207 will be described.

18 and 19, the hydraulic pump 207P of the hydrostatic stepless speed changer 207 is configured so as to be able to change steplessly to the neutral position N, the forward side F and the reverse side R . The shift lever 243 provided in the operation section 203 and the swash plate of the hydraulic pump 207P of the hydrostatic stepless speed change device 207 are mechanically connected to each other through the linkage link 280, The hydraulic pump 207P of the hydrostatic stepless speed changer 207 is moved to the neutral position N, the forward side F and the reverse side (i.e., the neutral position) by operating the swash plate of the hydraulic pump 207P of the hydrostatic stepless speed change device 207, R).

As shown in Figs. 18 and 19, the hydraulic motor 207M of the hydrostatic stepless speed changer 207 is configured to be able to change steplessly in the range of the lowest speed position L and the maximum speed position H, There is provided an operating cylinder 256 for operating the swash plate of the hydraulic motor 207M of the continuously-variable shifting device 207. [ A flow path 257 is connected to an oil chamber 256a through which the oil line 257 is branched from the charge flow path 245 to operate the operation cylinder 256 to the high speed side and the spring 256b for urging the operation cylinder 256 to the low speed side . The electromagnetic control type pressure control valve 258 is provided in the oil passage 257 so that when the pressure in the oil chamber 256a of the operation cylinder 256 rises, 256 operates on the high speed side and when the pressure in the oil chamber 256a of the operation cylinder 256 falls, the operation cylinder 256 is operated to the low speed side by the spring 256b of the operation cylinder 256. [

The travel shift switch 281 is provided below the transverse portion of the grip portion 243a of the shift lever 243 in the grip portion 243a on the upper side of the shift lever 243 . The travel change-over switch 281 is constituted by a lever switch type or a seesaw switch type configured to be operable at a neutral position, a high-speed position above and a low-speed position below and is pushed to a neutral position, Is input to the control device 279. [ A potentiometer 282 for detecting the position of the swash plate of the hydraulic motor 207M of the hydrostatic stepless speed change device 207 is provided so that the detection value of the potentiometer 282 is input to the control device 279, The operation section 203 is provided with a display section 287 for indicating the position of the swash plate of the hydraulic motor 207M of the hydrostatic stepless speed change device 207. [

Thereby, the pressure control valve 258 is operated by the control device 279 based on the operation of the travel shift switch 281, and the operation cylinder 256 is operated.

18, when the travel shift switch 281 is operated to the high speed position, the operating oil of the oil chamber 256a is supplied to the operating cylinder 256 by the pressure control valve 258 so that the operating cylinder 256 is operated at a high speed And the hydraulic motor 207M of the hydrostatic stepless speed changer 207 is operated to the high speed side. When the travel shift switch 281 is operated to the neutral position, the operating cylinder 256 is stopped by the pressure control valve 258 at this time, and the operation of the hydraulic motor 207M of the hydrostatic stepless transmission 207 is stopped And the position of the swash plate of the hydraulic motor 207M of the hydrostatic stepless speed change unit 207 is displayed on the display unit 287. [

18, when the travel shift switch 281 is operated to the low speed position, the operating oil in the oil chamber 256a is discharged to the operating cylinder 256 by the pressure control valve 258, The hydraulic motor 207M of the hydrostatic stepless speed changer 207 is operated to the low speed side. When the travel shift switch 281 is operated to the neutral position, the operating cylinder 256 is stopped by the pressure control valve 258 at this time, and the operation of the hydraulic motor 207M of the hydrostatic stepless transmission 207 is stopped And the position of the swash plate of the hydraulic motor 207M of the hydrostatic stepless speed change unit 207 is displayed on the display unit 287. [

Thus, by operating the travel shift switch 281 to the high or low speed position, the hydraulic motor 207M of the hydrostatic stepless speed changer 207 can be steplessly operated to the high speed side and the low speed side.

When the swash plate of the hydraulic motor 207M of the hydrostatic stepless speed changer 207 is operated to the high speed side beyond the previously set low speed setting position, the cut-off speed shift device 218 is automatically switched to the low speed position by an actuator . When the swash plate of the hydraulic motor 207M of the hydrostatic stepless speed change device 207 is operated to the low speed side beyond the low speed set position, the cut-off transmission 218 is automatically operated to the high speed position by the actuator.

The swash plate of the hydraulic motor 207M of the hydrostatic type stepless transmission 207 described above is operated to the low speed side beyond the low speed setting position and the state in which the sheathed transmission 218 is operated to the high speed position is the cutting operation Which corresponds to a case in which a crop of a crop reaches a severe portion.

[6]

The right and left side clutch 233 (the right and left engaging portions 228), the right and left circulating clutches 239, the relief clutch 236, the brakes 240, the reverse clutch 242 to the hydraulic unit 259 for operating the hydraulic oil.

16 and 17, the oil pressure unit 259 is connected to the lower portion of the left side of the transmission case 208. As shown in Fig. The hydraulic pump 260 is connected to the input shaft 207a of the hydrostatic stepless type speed changer 207 so that the hydraulic pump 260 is driven by the input shaft 207a of the hydrostatic stepless transmission 207, The oil passage 261 extending from the pump 260 is connected to the oil pressure unit 259.

17, the supply passage 262 is connected to the transmission case 208 and the hydraulic pump 260, the oil cooler 263 is provided in the supply passage 262, and the supply passage 262 is provided, A filter 264 is provided at a portion between the hydraulic pump 260 and the oil cooler 263 in the oil cooler 263. A bypass flow passage 265 is connected to a portion of the supply flow passage 262 on the side of the transmission case 208 and a portion between the oil cooler 263 and the filter 264 in the supply flow passage 262 And the flow path resistance of the bypass flow path 265 is smaller than the flow path resistance of the oil cooler 263.

17, the lubricating oil stored in the transmission case 208 passes through the oil cooler 263 and the bypass passage 265 as working oil, passes through the filter 264, (260). The operating oil of the hydraulic pump 260 is supplied to the oil pressure unit 259 through the oil passage 261 and the operating oil discharged from each part of the oil pressure unit 259 is returned to the mission case 208 as described later.

17, the oil pressure unit 259 includes a priority control valve 267, a left turn control valve 268, a first relief valve 269, an unload valve 270, a second relief valve 268, A proportional control valve 271, a swing switching control valve 272, and pilot operation valves 273 and 274 are provided. The oil passage 261 of the hydraulic pump 260 is connected to the oil pressure unit 259 and the right and left swing control valves 267 and 268 and the first relief valve 269 are connected to the oil passage 266 connected to the oil passage 261 And an unloading valve 270 are connected in parallel.

17, the priority control valve 267 is connected to the right side clutch 233 (the right engaging portion 228) and the right side revolving clutch 239, and the left turn control valve 268 are connected to the left side clutch 233 (left side engaging portion 228) and the left side rotating clutch 239. [ The right and left swing control valves 267 and 268 are configured to be electromagnetically operated by the supply positions 267a and 268a and the discharge positions 267b and 268b and are urged to the discharge positions 267b and 268b. The unloading valve 270 is electromagnetically operable to be operable with the shutoff position 270a and the discharge position 270b and is urged into the shutoff position 270a.

The second relief valve 276 is connected to the oil line 275 branched from the right and left side clutches 233 (the right and left engaging portions 228) 275 are connected in series to the proportional control valve 271 and the swing switching control valve 272 and the swing switching control valve 272 is connected in series with the complete clutch 236, the brake 240 and the reverse clutch 242 . The proportional control valve 271 is constituted by an electromagnetic operation so that the pressure of the operating oil can be controlled. The swing switching control valve 272 is of a pilot operated type which can be operated by the complete turn position 272a, the ground position 272b and the extrusion position 272c and is pushed by the complete turn position 272a have. In this case, the relief pressure of the first relief valve 269 is set to a relatively high value, and the relief pressure of the second relief valve 276 is set to a relatively low value.

17, the pilot operation valve 73 is configured to operate the pilot hydraulic fluid branched from the oil passage 275 to the swing switching control valve 272 to be operated at the pivot position 272b, and the oil passage 275 The pilot operation valve 274 is configured to supply the pilot operated hydraulic fluid branched from the hydraulic control valve 272 to the swing switching control valve 272 to operate the swing switching control valve 272 to the extension pivot position 272c. A drain passage (not shown) is formed on the connection surface (mating surface) between the hydraulic unit 259 and the mission case 208 and the first rotation control valve 267, the left rotation control valve 268, The operating fluid of the valve 269, the unloading valve 270, the second relief valve 276, the proportional control valve 271, the swing switching control valve 272 and the pilot operation valves 273, And returns to the case 208.

The right and left swing control valves 267 and 268, the unload valve 270, the proportional control valve 271 and the pilot control valves 273 and 274 are described in [7] [8] [9] [10] And is operated by the control device 279 as described above.

[7]

Next, the straight forward state by the steering lever 277 will be described.

As shown in Figs. 15 and 18, a steering lever 277, which is operable to the right and left, is provided in the operation section 203, and the operation position of the steering lever 277 is input to the control device 279 , The steering lever 277 is configured to be operable by the linear position N, right and left first pivot positions R1 and L1, and right and left second pivot positions R2 and L2. The turning mode switch 278 is provided in the operation unit 203 and the operating position of the turning mode switch 278 is inputted to the control device 279. The turning mode switch 278 is set to the full turn position, And an extreme pivot position.

16 to 18, when the steering lever 277 is operated to the straight forward position N regardless of the operating position of the turning mode switch 278, the right and left swing control valves 267, Positions 267b and 268b, and the unloading valve 270 is operated to the discharge position 270b. Thereby, the operating oil is discharged from the right and left side clutch 233 (right and left engaging portions 228) and the right and left rotating clutches 239, and the right and left side clutches 233 And the left engaging portion 228) are operated to the power transmission state, and the right and left revolving clutches 239 are operated in the reverse current state. The broken line and reverse clutches 236 and 242 are operated to the disconnected state by the proportional control valve 271 and the brake 240 is operated to the disengaged state.

The power of the output shaft 207b of the hydrostatic stepless speed changer 207 is transmitted to the low gear 210, the transmission gear 219, the transmission shaft 220, the transmission gear (not shown) Right and left output gears 227 and right and left transmission gears 230 and right and left axles 229 are connected to the left and right transmission gears 222 and 225, the transmission shaft 226, the right and left meshing portions 228, To the traveling device 201 on the right and left sides, and the gas goes straight.

[8]

Next, the state of complete turn by the steering lever 277 will be described.

16 to 18, when the turning mode switch 278 is operated to the complete turn position, the control valve 272 swung by the pilot operation valves 273 and 274 is moved to the complete turn position 272a . Thereby, when the steering lever 277 is operated to the right first pivotal position R1, the priority control valve 267 is operated to the supply position 267a and the unloading valve 270 is operated to the shutoff position 270a And the hydraulic oil is supplied to the right side clutch 233 (the right engaging portion 228) and the right side swing clutch 239 so that the right side clutch 233 (the right engaging portion 228) And the right side turning clutch 239 is operated in the electric state.

The power of the left side clutch 233 (the left engaging portion 228) is transmitted to the left output gear 227 and the left side gear 227 because the left side turning clutch 239 is in the inverted state, Is transmitted from the revolving clutch 239 of the left clutch 239 to the right output gear 227 through the right side turning clutch 239 so that the power in the same direction as the transmission shaft 226 and slightly lower in speed than the transmission shaft 226 is transmitted to the right output gear 227. [ (227). As a result, the gas gently changes direction to the right.

16 to 18, when the steering lever 277 is operated to the right first pivotal position R1, the priority control valve 267 is operated to the supply position 267a as described above, The hydraulic oil is supplied to the relief clutch clutch 236 through the proportional control valve 271 and the swing switching control valve 272 (the complete turn position 272a) while the hydraulic clutch 270 is operated to the cut position 270a And as the steering lever 277 is operated from the right first pivotal position R1 to the right second pivotal position R2, the operating pressure of the complete line clutch 236 is increased by the proportional control valve 271 do.

As shown in Figs. 16 to 18, when the operating pressure of the complete line clutch 236 is stepped up by the proportional control valve 271 based on the operating position of the steering lever 277, The transmission gear 238 and the swing clutch case 237 and the right swing clutch 239 and the left swing clutch 237. The power of the right clutch 229, the right clutch 228, the transmission gear 235, the loosening clutch 236, the transmission shaft 234, And is transmitted to the output gear 227 on the right side as a lower speed power than the transmission shaft 226.

16, the power from the left side clutch 233 (the left engaging portion 228) and the power from the relief clutch 236 are simultaneously transmitted to the right output gear 227. At this time, The power from the left side clutch 233 (the left engaging portion 228) is transmitted from the relieving clutch 236 to the power from the relieving clutch 236 when the operating pressure of the relieving clutch 236 is in the low pressure range, And the right output gear 227 is driven by the power from the left side clutch 233 (the left engaging portion 228). As a result, when the operating pressure of the fastening line clutch 236 is in the low pressure range, the gas gently changes direction to the right.

Next, when the operating position of the steering lever 277 approaches the right second pivotal position R2 and the operating pressure of the relief clutch clutch 236 becomes a high pressure, as shown in Fig. 16, The power is transmitted from the left side clutch 233 (the left engaging portion 228) and the right side output gear 227 is driven by the power from the complete line clutch 236. [ In this state, the power from the left side clutch 233 (the left engaging portion 228) causes the right side output gear 227 to be driven by the power from the complete side clutch 236, The output gear 227 of the right side is driven at a low speed and the base body is wound to the right side.

16 to 18, when the steering lever 277 is operated to the left first pivotal position L1, the left turn control valve 268 is operated to the feed position 268a and the unload valve 270 is operated, The operating oil is supplied to the left side clutch 233 (the left engaging portion 228) and the left side swing clutch 239 so that the left side clutch 233 (228) is operated in the cut-off state, and the left-hand rotating clutch 239 is operated in the electric state. At the same time, the above operation is performed, and the gas gently changes direction to the left. When the steering lever 277 is operated from the left first pivotal position L1 to the left second pivotal position L2, the above-described operation is performed, and the gas turns to the left side.

[9]

Next, a state in which the vehicle is turned by the steering lever 277 will be described.

16 to 18, when the turning mode switch 278 is operated to the ground position, the pilot control valves 273 and 274 operate the swing switching control valve 272 to the ground pivot position 272b do.

Thereby, when the steering lever 277 is operated to the right first pivotal position R1, the priority control valve 267 is operated to the supply position 267a and the unloading valve 270 is operated to the shutoff position 270a The operating oil is supplied to the right side clutch 233 (right side engaging portion 228) and the right side rotating clutch 239 so that the right side clutch 233 (right side engaging portion 228) And the right side turning clutch 239 is operated in the electric state. In this case, since the left swing clutch 239 is in an inverted state, the vehicle gently changes its direction to the right as described in [8].

16 to 18, when the steering lever 277 is operated to the right first pivotal position R1, the priority control valve 267 is operated to the supply position 267a as described above, The operating fluid is started to be supplied to the brake 240 via the proportional control valve 271 and the swing switching control valve 272 (the pivot position 272b) at the same time that the operating fluid 270 is operated to the blocking position 270a And the operating pressure of the brake 240 is stepped up by the proportional control valve 271 as the steering lever 277 is operated from the right first pivot position R1 to the right second swivel position R2.

16 to 18, when the operating pressure of the brake 240 is stepped up by the proportional control valve 271 based on the operating position of the steering lever 277A, A braking force is applied to the right output gear 227 via the transmission gear 238, the swing clutch case 237 and the right swing clutch 239. [

In this case, as shown in Fig. 16, the state in which the power from the left side clutch 233 (the left engaging portion 228) and the braking force of the brake 240 are simultaneously transmitted to the right output gear 227 The power from the left side clutch 233 (the left side engaging portion 228) overcomes the braking force of the brake 240 and is transmitted to the left side clutch 233 when the operating pressure of the brake 240 is low. The right output gear 227 is driven by the power from the [left engagement portion 228]. Thus, when the operating pressure of the brake 240 is in the low pressure range, the gas gently changes direction to the right.

Next, when the operating position of the steering lever 277 approaches the right second pivotal position R2 and the operating pressure of the brake 240 becomes high, the braking force of the brake 240 is transmitted to the left side The power from the clutch 233 (the left engaging portion 228) is applied so that the output gear 227 on the right side is in a braking state by the braking force of the brake 240, and the vehicle is pivoted to the right.

16 to 18, when the steering lever 277 is operated to the left first pivotal position L1, the left turn control valve 268 is operated to the feed position 268a and the unload valve 270 is operated, The operating oil is supplied to the left side clutch 233 (the left engaging portion 228) and the left side swing clutch 239 so that the left side clutch 233 The engaging portion 228) is operated to the disconnected state, and the left swing clutch 239 is operated to the electric state. At the same time, the above operation is performed, and the gas gently changes direction to the left. When the steering lever 277 is operated from the left first pivotal position L1 to the left second pivotal position L2, the above-described operation is performed, and the base body pivots to the left.

[10]

Next, the steering wheel turning state by the steering lever 277 will be described.

When the swing mode switch 278 is operated to the extreme pivot position as shown in Figs. 16 to 18, the swing switching control valve 272 is depressed by the pilot control valves 273 and 274 to the swing pivot position 272c, .

Thereby, when the steering lever 277 is operated to the right first pivotal position R1, the priority control valve 267 is operated to the supply position 267a and the unloading valve 270 is operated to the shutoff position 270a The operating oil is supplied to the right side clutch 233 (the right engaging portion 228) and the right side swing clutch 239 so that the right side clutch 233 (the right engaging portion 228) And the right side swing clutch 239 is operated to the electric state. In this case, since the left swing clutch 239 is in the inverted state, the vehicle gently changes its direction to the right as described in [8].

16 to 18, when the steering lever 277 is operated to the right first pivotal position R1, the priority control valve 267 is operated to the supply position 267a and unloaded The hydraulic oil is supplied to the reverse rotation clutch 242 via the proportional control valve 271 and the swing switching control valve 272 (the extension position of the swing pivot position 272c) at the same time that the valve 270 is operated to the shutoff position 270a And as the steering lever 277 is operated from the right first pivot position R1 to the right second pivot position R2, the operating pressure of the reverse clutch 242 is reduced by the proportional control valve 271 Up operation.

16 to 18, the operating pressure of the reverse rotation clutch 242 is stepped up by the proportional control valve 271 based on the operating position of the steering lever 277, Is transmitted through the transmission gears 223 and 241, the reverse rotation clutch 242, the transmission shaft 234, the transmission gear 238, the swing clutch case 237 and the right swing clutch 239, 226 and the right side output gear 227 as a reverse power.

In this case, the power from the left side clutch 233 (the left engaging portion 228) and the power from the reverse rotation clutch 242 are simultaneously transmitted to the right output gear 227 The power from the left side clutch 233 (the left engaging portion 228) is transmitted to the reverse clutch 242 from the reverse clutch 242 when the operating pressure of the reverse clutch 242 is low. And the right output gear 227 is driven by the power from the left side clutch 233 (the left engaging portion 228). Thus, when the operating pressure of the reverse rotation clutch 242 is in the low pressure range, the gas gently changes direction to the right.

Next, when the operating position of the steering lever 277 approaches the right second pivotal position R2 and the operating pressure of the reverse rotation clutch 242 becomes high, as shown in Fig. 16, The power is supplied from the left side clutch 233 (the left engaging portion 228), and the right output gear 227 is driven by the power from the reverse rotation clutch 242. [ In this state, the output gear 227 on the right side is driven in the reverse direction with respect to the left output gear 227, and the base body is pivoted to the right side.

16 to 18, when the steering lever 277 is operated to the left first pivotal position L1, the left turn control valve 268 is operated to the feed position 268a and the unload valve 270 is operated, The operating oil is supplied to the left side clutch 233 (the left engaging portion 228) and the left side swing clutch 239 so that the left side clutch 233 The engaging portion 228) is operated to the disconnected state, and the left swing clutch 239 is operated to the electric state. At the same time, the above operation is performed, and the gas gently changes direction to the left. When the steering lever 277 is operated from the left first pivotal position L1 to the left second pivotal position L2, the above-described operation is performed, and the base body is pivoted to the left.

[Other aspect 1 of the third embodiment]

The hydraulic motor 207M of the hydrostatic stepless speed changer 207 is not steplessly operated to the high speed side and the low speed side as described above but the hydraulic motor (not shown) of the hydrostatic stepless speed changer 207 is operated by the operating cylinder 256 207M may be operated by a plurality of operating positions (for example, five operating positions).

In this case, a plurality of operation positions can be arbitrarily changed and stored according to the preference of the driver, and one of the plurality of operation positions can be selected by operating an operation switch (not shown).

When the selected low speed setting position is compared with the selected operating position and the selected operating position is higher than the low speed predetermined position, the cut shear transmission 218 is automatically operated to the low speed position by an actuator (not shown) When the selected operating position is at a lower speed than the predetermined position at low speed, the cut-off transmission 218 is configured to be automatically operated by the actuator to the high speed position.

[Another form 2 of the third embodiment]

The hydraulic motor 207M of the hydrostatic stepless speed changer 207 is moved by the operating cylinder 256 to the high speed position for traveling, the medium speed position for cutting work, And a low-speed position for work.

In this case, an actuator (not shown) for operating the cut-off transmission 218, a cutting clutch (not shown) capable of transmitting and cutting the power transmitted to the traveling device 202, and an actuator (Not shown) and a cut-off gearshift switch (not shown) provided in the grip portion 243a (see FIG. 18) of the shift lever 243, The cut-off clutch may be configured to be automatically operated as follows.

As shown in Fig. 20, the running state, the standard cutting state, and the low-speed cutting state are set in the control device 279. [

The shift running state is a state in which the hydraulic motor 207M of the hydrostatic stepless speed change device 207 is operated to the high speed position, the cut clutch is operated to the cutoff state, and the cut shear transmission 218 is operated to the low speed position. The standard cut state is a state in which the hydraulic motor 207M of the hydrostatic stepless speed changer 207 is operated to the medium speed position, the cut clutch is operated to the power transmission state, and the cut-off transmission 218 is operated to the low speed position. In the low-speed cut state, the hydraulic motor 207M of the hydrostatic stepless transmission 207 is operated to the low speed position, the cut clutch is operated to the power transmission state, and the cut-off transmission 218 is operated to the high speed position.

As shown in Fig. 20, when the travel shift switch is depressed in the state in which the travel shift state is set, the standard cut state is set, and when the travel shift switch is depressed in the state where the standard cut state is set, State is set. Thus, the traveling state and the standard cutting state are alternately set each time the travel shift switch is pressed.

In this case, even if the cut-sheet shifting switch is pressed in the state that the traveling state is set, the pressing operation is ignored and the traveling state is maintained. In the state in which the standard cutting state is set by pressing operation of the traveling speed change switch, the low speed cutting state is set when the work cutting speed change switch is pressed.

As shown in Fig. 20, in the state that the standard cut condition is set, when the cut-off shift switch is pressed, the low cut condition is set. If the cut-off shifting switch is pressed while the low-speed cutting state is set, the standard cutting state is set. The standard cutting condition and the low-speed cutting condition are alternately set each time the cut-off shifting switch is depressed.

In this case, even if the transmission shift switch is pressed while the low-speed cutting state is set, this pressing operation is ignored and the low-speed cutting state is maintained. When the coasting shift switch is depressed to set the standard cut state, when the travel shift switch is depressed, the travel running state is set.

[Another Mode 3 of Third Embodiment]

The following configuration may be provided in the above-described configuration.

18 and 21, when hydraulic oil of the oil chamber 256a is suddenly operated by the operation shift switch 281 and the pressure control valve 258 to the operation cylinder 256, The pressure of the oil chamber 256a is manipulated in the range of the minimum pressure B1 and the maximum pressure B2. The position of the swash plate of the hydraulic motor 207M of the hydrostatic stepless speed changer 207 and the pressure of the oil chamber 256a of the operating cylinder 256 are set to a predetermined value in a no-load state in which no load is applied to the hydrostatic stepless transmission 207, And the lowest pressure B1 of the oil chamber 256a of the operating cylinder 256 is the lowest speed position of the hydraulic motor 207M (swash plate) of the hydrostatic stepless speed changer 207 And the maximum pressure B2 (set by the relief valve 250 (see Fig. 19)) of the oil chamber 256a of the operating cylinder 256, which corresponds to the hydraulic pressure L of the hydrostatic stepless speed change device 207, Corresponds to the maximum speed position (H) of the drive shaft 207M (swash plate).

As shown in Fig. 21, when the swash plate of the hydraulic motor 207M of the hydrostatic stepless transmission 207 is maintained at a predetermined pressure in a state where the pressure of the oil chamber 256a of the operating cylinder 256 is maintained at the predetermined pressure When the load applied to the hydrostatic stepless speed changer 207 increases, the swash plate of the hydraulic motor 207M of the hydrostatic stepless speed changer 207 is displaced to the low speed side by the load. The relationship between the position of the swash plate of the hydraulic motor 207M of the hydrostatic stepless speed changer 207 and the pressure of the oil chamber 256a of the operating cylinder 256 according to the load applied to the hydrostatic stepless speed changer 207 (A2, A3, etc.) are already known.

As shown in Fig. 21, in the state in which the pressure in the oil chamber 256a of the operating cylinder 256 is maintained at a predetermined pressure, the pressure of the hydraulic oil in the hydrostatic stepless transmission 207 (see Fig. 18) (A1, A2, A3, and the like) by detecting the position of the swash plate of the hydraulic motor 207M of the hydraulic motor 207M of the hydraulic motor 207M to detect the load applied to the hydrostatic stepless speed change device 207 have. The load on which the relief valve 286 shown in Fig. 19 is opened is also grasped in advance.

As described above, by the pressure of the oil chamber 256a in the operating cylinder 256 and the position of the swash plate of the hydraulic motor 207M of the hydrostatic stepless speed changer 207, When the load is detected, the hydraulic motor 207M of the hydrostatic stepless transmission 207 is rotated until the load on the hydrostatic stepless speed changer 207 reaches a load slightly smaller than the load on which the relief valve 286 is opened. The position of the swash plate of the motorcycle 1 is not changed. When the load applied to the hydrostatic stepless speed change device 207 reaches a load slightly smaller than the load at which the relief valve 286 is opened, the hydraulic cylinder 207M of the hydrostatic stepless transmission 207 is rotated by the operating cylinder 256 at a low speed The state in which the relief valve 286 is opened is avoided.

[Other aspect 4 of the third embodiment]

22, a continuously variable transmission type transmission device 288 (including a belt type continuously variable transmission or a Troydal core type continuously variable transmission (not shown)) is connected to the output shaft 207b (hydraulic motor 207M) of the constant hydraulic oil type continuously variable transmission device 207, Device or the like) may be connected.

22, the output shaft 207b (hydraulic motor 207M) of the hydrostatic stepless speed changer 207 is not operated, but the output shaft 207b (hydraulic motor 207M) of the hydrostatic stepless speed changer 207 is operated, instead of operating the hydraulic motor 207M of the hydrostatic stepless speed changer 207, To transmit the power of the transmission 288 to the transmission 288 so as to transmit the power of the transmission 288 from the transmission shaft 212 to the shear transmission 218 and the transmission shaft 220 .

[Other aspect 5 of the third embodiment]

The above-described cutting machine transmission 218 may be configured as a continuously variable transmission type (a constant oil hydraulic type continuously variable transmission, a belt type continuously variable transmission, a Troydal core type continuously variable transmission, or the like).

[Fourth Embodiment]

Next, a fourth embodiment will be described with reference to Figs. 23 to 30. Fig.

[One]

As shown in Fig. 23, the support frame 302 is supported on the front portion of the base supported by the right and left crawler type traveling devices 301 so as to be vertically movable around the axis of abscissa X, A single hydraulic cylinder 303 (corresponding to a lifting mechanism) for lifting and lowering the support frame 302 is provided. A driving unit 305 is provided on the right side of the front part of the base body and a balancing device 307 is provided on the left side of the rear part of the base body and a grain tank 308 is provided on the right side of the rear part of the base, Combination of phosphorus demolding is composed.

23 and 24, a front panel 309 is provided in front of the driver's seat 306 in the operation unit 305 and a driver's seat 306 is provided from the left side of the front panel 309. [ The side panel 310 is provided on the left side of the side panel 310. [ A liquid crystal panel 311 for performing various displays is provided at a central portion of the front panel 309. An operation lever 312 (corresponding to the elevating operation opening and the first elevating opening opening) is provided on the right side of the front panel 309, And a selection dial 318 in a pivot state.

23 and 24, a mounting table 324 fixed to the front panel 309 is disposed on the rear side of the operation lever 312, so that a driver sitting on the driver's seat 306 can move his or her right hand The holding portion 312a of the operation lever 312 can be held while being placed on the table 324. And a shift lever 313 for operating a stepless hydraulic type continuously variable transmission (not shown) for running is provided on the front portion of the side panel 310. On the right side of the shift lever 313 in the side panel 310, A setting dial 314 (corresponding to the changing means) is provided.

[2]

Next, the steering operation of the gas by the operation lever 312 will be described.

As shown in Figs. 24 and 25, the operation lever 312 is movable in the forward and backward directions (upward position U (downward in Fig. 24) and downward position D (upward in Fig. 24) (The first and second pivot positions R1 and R2 on the right side and the first and second pivot positions L1 and L2 on the left side) And the operation position of the operation lever 312 is inputted to the control device 315. [ The selection dial 318 is configured so as to be operable artificially with the full turn position, the full turn position, and the full turn position, and the operation position of the select dial 318 is inputted to the control device 315. [

A right side clutch (not shown) that can transmit and block the power to the right traveling device 301, a left side clutch (not shown) that can transmit and block the power to the left traveling device 301, (Not shown) that drives the traveling device 301 on the left side in the same direction at a lower speed than the traveling device 301 on the left (right) side, And a reverse rotation mechanism (not shown) for driving the traveling device 301 on the right (left) side in the reverse direction of the traveling device 301 on the left (right) side are provided have.

The control device 315 controls the operation lever 312 by operating the first and second pivotal positions R1 and R2 on the right side and the first and second pivotal positions L1 and L2 on the left side, The clutch, the loosening mechanism, the braking mechanism, and the reverse rotation mechanism are operated as follows.

25, when the operation lever 312 is operated to the neutral position N, the right and left side clutches are operated to the electric state, and the right and left traveling devices 301 are moved in the same direction The gas is driven at the same speed and travels straight. When the operation lever 312 is operated to the right first pivotal position R1 (left first pivotal position L1), the right side (left) side clutch is operated to the disconnected state, and the right The traveling device 301 is in a freely rotatable state, and the base body gently changes direction to the right (left) side.

The operation lever 312 is moved to the second pivotal position R2 on the right side (the second pivotal position L2 on the left side) in a state in which the selection dial 318 is operated to the full stroke position, The left-side traveling device 301 is driven in the same direction at a lower speed than the left-side traveling device 301, and the gas is returned to the right (left) side .

When the operation lever 312 is operated to the right second swivel position R2 (left second swivel position L2) while operating the selection dial 318 to the stop position, the braking mechanism is operated, The braking force is applied to the traveling device 301 on the side of the vehicle, and the vehicle is pivoted to the right (left) side.

When the operation lever 312 is operated to the right second swivel position R2 (left second swivel position L2) while the selection dial 318 is operated to the extended position, the reverse rotation mechanism is operated The traveling device 301 on the right (left) side is driven in the direction opposite to the traveling device 301 on the left (right) side, and the vehicle turns to the right (left) side.

The right steering switch 316 and the left steering switch 317 are provided on the upper portion of the grip portion 312a of the operation lever 312 and the operation of the right and left steering switches 316 and 317 A signal is input to the control device 315. [ When the right steering switch 316 is depressed (the depressing operation is performed by depressing the depressing operation), the right side side clutch is operated to the disconnected state and is immediately operated to the electric state. When the depressing operation of the left steering switch 317 is performed , The left side clutch is operated to the disconnected state and is immediately operated to the electric state.

[3]

Next, the elevating structure of the preloading section 304 will be described.

As shown in Fig. 25, the hydraulic cylinder 303 is provided with a control valve 319 for operating and operating the hydraulic oil, and the control valve 319 is operated by the control device 315. Fig. When the control valve 319 is operated to the up position, the hydraulic oil is supplied from the control valve 319 to the hydraulic cylinder 303, and the hydraulic cylinder 303 is extended to raise the preload portion 304. When the control valve 319 is operated to the lowered position, the hydraulic oil is discharged from the hydraulic cylinder 303 by the control valve 319 and the hydraulic cylinder 303 is contracted to lower the preloading portion 304. When the control valve 319 is operated to the neutral position, the supply and discharge of hydraulic oil is cut off by the control valve 319, and the hydraulic cylinder 303 and the preloading portion 304 stop.

23 and 25, a height sensor 320 for detecting the vertical angle of the support frame 302 with respect to the base is provided and the detection value of the height sensor 320 is input to the control device 315 And the height of the preload portion 304 with respect to the base is detected by the detection value of the height sensor 320. [ The elevating switch 321 (corresponding to the elevating operation opening and the second elevating opening) is provided on the upper portion of the gripping portion 312a of the operation lever 312 and the operation signal of the elevating switch 321 is supplied to the control device 315 Respectively.

As shown in Fig. 25, the setting dial 314 has an OFF position, a first falling limit D1, a second falling limit D2, a third falling limit D3, a fourth falling limit D4, The fifth falling limit D5, and the sixth falling limit D6, and the operation position of the setting dial 314 is inputted to the control device 315. [

[4]

Next, the elevation of the preloading section 304 by the operation lever 312 will be described with reference to Fig. 26 in a state where the setting dial 314 is operated to the OFF position (corresponding to the stop state of the changing means) .

When the control lever 311 is operated to the raised position U (step S2) while the setting dial 314 shown in Fig. 25 is operated to the OFF position (step S1) (Step S4), and the hydraulic cylinder 303 is operated to extend to raise the preload part 304. As a result, The control valve 319 is operated to the lowered position (step S6), the hydraulic cylinder 303 is contracted and the preloaded portion 304 is moved to the lowered position D Descend. When the operation lever 312 is operated to the neutral position N (step S2), the control valve 319 is operated to the neutral position (step S7), and the hydraulic cylinder 303 and the preload part 304 stop The control means and the first control means).

The upper limit UU1 (the upper limit of the hydraulic cylinder 303) and the upper limit of the upper limit UU2 (the upper limit of the hydraulic cylinder 303) Slightly lower than the mechanical extension limit] and the lowering limit DD1 (slightly above the mechanical shrinkage limit of the hydraulic cylinder 303).

In this case, as shown in Fig. 28, in a state in which the right and left traveling apparatuses 301 are grounded on a flat and hard agricultural land G (ground) (the traveling apparatus 301 on the right and left sides is a farmland surface Is set to be lower than the farmland surface G (ground) in the state in which the landing surface G is not sunk (drawn) on the land G (ground).

When the height sensor 320 detects that the preloading portion 304 has reached the elevation limit UU1 in a state where the operation lever 312 is being operated to the elevation position U (Steps S1, S2, S4) (Step S3), the control valve 319 is operated to the neutral position (Step S7), and the preloading portion 304 stops at the rising limit UU1.

When the height sensor 320 detects that the preloading portion 304 has reached the falling limit DD1 in a state where the operation lever 312 is being operated to the lowering position D (Steps S1, S2, S6) (Step S5), the control valve 319 is operated to the neutral position (step S7), and the preload part 304 stops at the falling limit DD1.

The first lift range A1 of the lift limit UU1 and the fall limit DD1 is set by operating the operation lever 312 while the setting dial 314 is operated to the OFF position, (Corresponding to the control means and the first control means), the preload portion 304 can be raised and lowered, and can be stopped at an arbitrary intermediate position.

[5]

Next, with reference to FIG. 26, the elevation of the preloading section 304 by the elevation switch 321 in a state where the setting dial 314 is operated to the OFF position (corresponding to the stopping state of the changing means) do.

The first to sixth falling limits D1 to D6 in the vicinity of the falling limit DD1 are set so as to correspond to the first to sixth falling limits D1 to D6 of the setting dial 314, ) Is set. In the first to sixth falling limits D1 to D6, the first falling limit D1 is the lowest position and the sixth falling limit D6 is the highest position.

In this case, as shown in Fig. 28, in a state in which the right and left traveling apparatuses 301 are grounded on a flat and hard agricultural land G (ground) (the traveling apparatus 301 on the right and left sides is a farmland surface The first falling limit D1 is set to be lower than the farmland surface G (ground), and the first falling limit D1 is set to be lower than the falling limit DD1 As shown in FIG.

In a state where the setting dial 314 shown in Fig. 25 is operated to the OFF position (step S1) and the operating lever 312 is operated to the neutral position N or the down position D (step S2) (Step S8). If the preloading section 304 is located in the elevation limit UU1 (step S9), the control valve 319 is moved to the lowered position (Step S10), the hydraulic cylinder 303 contracts to lower the preload part 304, and when the preload part 304 reaches the second lowering limit D2, the height sensor 320 (Step S12), the control valve 319 is operated to the neutral position (Step S13), and the preloading portion 304 stops at the second falling limit D2 (corresponding to the second control means) (Corresponding to a state in which the falling limit of the second control means is set above the falling limit of the first control means in the stop state of the changing means).

In this case, as shown in Fig. 28, in a state in which the right and left traveling apparatuses 301 are grounded on a flat and hard agricultural land G (paper surface) (the traveling apparatus 301 on the right- The second lowering limit D2 is set to be substantially the same as the agricultural land G (ground) (or in the state where the agricultural land G is not grounded ) &Quot;). The second lowering limit D2 may be changed to the third lowering limit D3 or the fourth lowering limit D4 in step S12 of Fig.

The operation proceeds to steps S1 to S7 described in the preceding paragraph [4] after the preload section 304 is stopped at the second falling limit D2 by the depressing operation of the elevation switch 321. By the operation lever 312 The preloading section 304 can be lowered from the second lowering limit D2 to the lowering limit DD1 and the preloading section 304 can be raised from the second lowering limit D2 to the upper limit UU1 (Equivalent to the first control means).

In a state where the setting dial 314 shown in Fig. 25 is operated to the OFF position (step S1) and the operation lever 312 is operated to the neutral position N or the down position D, (Step S8). If the preloading section 304 is not located in the rising limit UU1 (step S9), the control valve 319 is operated to the up position (Step S14) and the hydraulic cylinder 303 is extended to raise the preload part 304. When the height sensor 320 detects that the preload part 304 has reached the upper limit UU1 S15), the control valve 319 is operated to the neutral position (step S13), and the preloading section 304 stops at the rising limit UU1 (equivalent to the second control means).

As shown in Fig. 28, when the setting dial 314 is operated to the OFF position, the second lift range (UU1) and the second lift limit (D2) of the lift limit UU1 and the second fall limit D2 It is possible to raise and lower the preload portion 304 in the first and second control means A2 (control means and second control means). The upper limit UU1 of the first lift limit A1 and the upper limit UU1 of the second lift range A2 coincide with each other in the first and second lift ranges A1 and A2, The second lowering limit D2 of the second lift range A2 is located above the lowering limit DD1 of the limit A1.

In the state in which the operation lever 312 is operated to the raised position U and the preloading section 304 is raised (steps S1, S2, and S4), this state is preferential and the process proceeds to step S8. 321 are pressed, the operations in steps S9 to S15 are not performed.

When the operation lever 312 is operated to the raised position U (step S11) during the descent of the preload part 304 in steps S9 to S12, the process proceeds to steps S1, S2 and S4, (Step S4), the hydraulic cylinder 303 is operated to extend and the preloading section 304 is moved upward. Thereafter, the process proceeds to steps S1 to S7 as described in the preceding paragraph [4].

[6]

Next, in a state where the setting dial 314 is operated to the first to sixth falling limits D1 to D6 (corresponding to the operating state of the changing means), the operation lever 312 The elevating and lowering will be described with reference to Fig.

When the operation lever 312 is operated to the raised position U (step S1) when the setting dial 314 shown in Fig. 25 is operated to the first to sixth falling limits D1 to D6 S21), the control valve 319 is operated to the up position (step S23), the hydraulic cylinder 303 is operated to extend, and the preload part 304 rises. The control valve 319 is operated to the lowered position (step S25), the hydraulic cylinder 303 is contracted and the preloaded portion 304 is moved to the lowered position D Descend. When the operation lever 312 is operated to the neutral position N (step S21), the control valve 319 is operated to the neutral position (step S26), and the hydraulic cylinder 303 and the preload part 304 stop Or more, equivalent to the first control means).

When the height sensor 320 detects that the preloading section 304 has reached the elevation limit UU1 in a state where the operation lever 312 is operated to the elevation position U (steps S1, S21, S23) Step S22), the control valve 319 is operated to the neutral position (step S26), and the stopping unit 304 stops at the rising limit UU1.

For example, as shown in Fig. 29, in a state where the third falling limit D3 is set by the setting dial 314, when the operation lever 312 is operated in the lowered position D When the height sensor 320 detects that the preloading portion 304 has reached the third falling limit D3 (Step S24), the control valve 319 is operated to the neutral position (Step S26), and the preload part 304 stops at the third falling limit D3.

29, in the state where the setting dial 314 is operated to the first to sixth falling limits D1 to D6, by operating the operation lever 312, the rising limit UU1 and the first to sixth falling limits It is possible to raise and lower the preload portion 304 in the first lift range A1 (corresponding to the first control means) of the sixth falling limits D1 to D6, . In this case, one of the first to sixth falling limits (D1 to D6) can be arbitrarily selected in step S24 by operating the setting dial 314.

[7]

Next, in a state where the setting dial 314 is operated to the first to sixth falling limits D1 to D6 (corresponding to the operating state of the changing means), the elevation switch 321 moves the pre- The elevating and lowering will be described with reference to Fig.

For example, as shown in Fig. 29, the third falling limit D3 is set by the setting dial 314 (step S1), and the operation lever 312 is moved to the neutral position N or the lowering position (Step S27). If the preloading section 304 is located in the elevation limit UU1 (step S28), the elevation switch 321 is depressed The control valve 319 is operated to the lowered position (step S29) and the hydraulic cylinder 303 contracts to lower the preloading section 304. When the preloading section 304 reaches the third lowering limit D3 (Step S31), the control valve 319 is operated to the neutral position (step S32), and the preload part 304 stops at the third falling limit D3 , Corresponding to second control means).

Even after proceeding to steps S1 and S21 to S26 described in the preceding paragraph [6] after the preliminary mounting section 304 has stopped at the third falling limit D3, the preliminary mounting section 304 is moved to the third falling limit D3 It can not be lowered.

The operation lever 312 is moved to the neutral position N or the downward position D by operating the setting dial 314 shown in Fig. 25 to the first to sixth falling limits D1 to D6 (step S1) (Step S27). If the elevation switch 304 is not located in the elevation limit UU1 (step S28) The valve 319 is operated to the lifted position (step S33), the hydraulic cylinder 303 is extended and the preloading section 304 is lifted, and the fact that the preloading section 304 reaches the upper limit UU1 (Step S34), the control valve 319 is operated to the neutral position (step S32), and the stopping section 304 stops at the rising limit UU1 .

29, in a state in which the setting dial 314 is operated to the first to sixth falling limits D1 to D6, the elevation limit UU1 and the first The elevation range 304 can be raised and lowered in the second lift range A2 (control means and second control means) of the sixth falling limits D1 to D6.

In this case, one of the first to sixth falling limits D1 to D6 can be arbitrarily selected in step S31 by operating the setting dial 314. The upper limit UU1 of the first lift limit A1 and the upper limit UU1 of the second lift range A2 coincide in the first and second lift ranges A1 and A2, The first to sixth falling limits D1 to D6 of the first lift range A1 coincide with the first to sixth falling limits D1 to D6 of the second lift range A2.

In a state in which the operation lever 312 is operated to the elevated position U and the preloading section 304 is elevated (steps S1, S21 and S23), this state is preferential and the operation does not proceed to step S27. 321 are pressed, the operations in steps S28 to S34 are not performed.

When the operation lever 312 is operated to the raised position U (step S30) during the descent of the preload part 304 in steps S28 to S31, the process proceeds to steps S1, S21 and S23, and the control valve 319 (Step S23), the hydraulic cylinder 303 is operated to extend, and the preload portion 304 rises. Thereafter, the flow advances to steps S1 and S21 to S26 as described in the preceding paragraph [6].

[Other aspect 1 of the fourth embodiment]

The lift switch 321 of FIG. 25 is abolished and the lift switch 322 (corresponding to the lift operation opening and the second lift operation opening) provided with only the lift function of the lift switch 321, as shown in FIG. 30, And a lowering switch 323 (corresponding to the elevating operation opening and the second elevating opening opening) having only the lowering function of the elevating switch 321 may be provided on the upper portion of the holding portion 312a of the operation lever 312 .

In this case, the lifting switch 321 and the lifting / lowering switches 322 and 323 may be provided at positions other than the operating lever 312 (for example, the front panel 309 and the side panel 310).

Thus, steps S14, S15, and S13 of FIG. 26 and steps S33, S34, and S32 of FIG. 27 are performed when the lifting switch 322 is pressed (pressed and returned) (Pressing and returning operation), the steps S10 to S13 of FIG. 26 and the steps S29 to S32 of FIG. 27 are performed.

[Another form 2 of the fourth embodiment]

The first to sixth falling limits D1 to D6 of the first lift limit A1 and the first to sixth falling limits D1 to D6 of the second lift range A2 coincide with each other in the above- The first to sixth falling limits D1 to D6 of the first lift limit A1 and the first to sixth falling limits D1 to D6 of the second lift range A2 are separately set Independent) high or low.

[Other aspect 3 of the fourth embodiment]

The upper limit position UU1 of the first lift limit A1 and the upper limit position UU1 of the second lift limit range A2 may be configured to be changed to the high and low positions while maintaining the same position . The upper limit position UU1 of the first lift limit A1 and the upper limit position UU1 of the second lift limit A2 may be separately and independently changed.

[Another aspect 4 of the fourth embodiment]

A height sensor (grounding sled bending type or ultrasonic sensor type) (not shown) for detecting the height from the farmland surface G (ground) to the preloading portion 304 is provided in the above- And a cut-off height control means for automatically expanding and contracting the hydraulic cylinder 303 so that the preload portion 304 is maintained at a set height from the farmland surface G (ground) based on the detected value of the height sensor .

In this case, after the preloading section 304 is lowered by the operation lever 312, the elevation switch 321 and the lowering switch 323, the cutting height control means is configured to automatically start the operation when entering the cutting stroke For example, a base motion sensor (not shown) for detecting that the curved surface of the agricultural paper surface G (paper surface) is drawn into the preloading portion 304 is provided below the front portion of the preload portion 304, It is judged that the cutting operation has been entered.

[8]

The description of the fourth embodiment and other forms is as described above.

In the cutting and harvesting machine, the cutting part is advanced while being positioned on the agricultural surface (slightly above the agricultural surface), and once the cutting process is completed and the gas reaches the bottom part of the machine, . When the turn at the slug is finished, the cutting part is lowered to the agricultural surface and the next cutting operation is executed.

In this case, if there is irregularity on the farmland surface, the leading end portion (for example, a divider) of the pre-loading portion may protrude into the convex portion of the farmland surface to be damaged, It is necessary to set the height of the preloaded portion of the farmland so that it does not occur. Particularly, when the turning at the boggle is completed and the cut part is lowered to the farmland to enter the next cut, the driver needs to pay attention to the height of the preload part against the farmland.

For this purpose, in the first aspect of the fourth embodiment, the preload portion 304 is provided so as to be movable up and down on the front portion of the base body. A hydraulic cylinder 303 as an elevating mechanism for elevating and lowering the preloading section 304, and an operation lever 312 as an elevating operation opening (first elevating opening) to be manipulated artificially. The operation of the operation lever 312 causes the hydraulic cylinder 303 to be operated to the upward side and the downward side in the range of the upward limit UU1 set to the upper direction and the downward limit DD1 set downward, (First control means) for stopping operation of the hydraulic cylinder 303 by the operation of the control means. And a setting dial 314 as a changing means for changing the falling limit DD1 of the control means (first control means) to high and low.

According to the above configuration, the preloading section 304 can be raised and lowered by the operation of the operation lever 312, and the preloading section 304 can be stopped at an arbitrary position by the operation of the operation lever 312 have. In this case, since the lowering limit DD1 is set, when the operation lever 312 is operated to lower the preloading unit 304, the preloading unit 304 is lowered beyond the lowering limit DD1 I can not. Then, the descent limit DD1 can be changed to high and low.

When the irregularities of the farmland surface are relatively large, the lowering limit DD1 may be set to the upper side. Thus, for example, when the turning of the bobbin 304 is completed and the preloading section 304 is lowered to the farmland surface to enter the next machining stroke, the operation lever 312 rotates the preloading section 304 down to the lowering limit DD1 It is possible to avoid a state in which the leading end portion of the preloading portion 304 enters into the convex portion of the farmland surface when the cutting is performed after this time because the height of the preloading portion 304 is secured with respect to the farmland surface. Therefore, when the turning of the bogies is completed and the preloading unit 304 is lowered to the farmland surface to enter the next cutting cycle, it is unnecessary to pay more attention to the height of the preloading unit 304 with respect to the farmland surface.

If the lowering limit DD1 is set to the upper side in the case where the irregularities of the farmland surface are relatively large, for example, in the cutting process, the operation of the operation lever 312 causes the preloading portion 304 to follow the farmland surface Even if the operation lever 312 is raised or lowered and the operator tries to lower the preload portion 304 by mistake by operating the operation lever 312, the preload portion 304 stops at the downward limit DD1, It is possible to avoid a state in which the leading end portion rushes into the convex portion of the farmland surface.

Therefore, in the ascending / descending structure of the preloading portion 304, for example, when the turning of the preloading portion 304 is finished and the preloading portion 304 is lowered to the farmland surface to enter the next cutting operation, It is possible to reduce the state of entering into the convex portion of the agricultural land, thereby improving the cutting performance of the cutting and harvesting machine.

In the cutting operation, for example, in the state in which the preloading portion 304 is raised and lowered along the farmland surface by the operation of the operation lever 312, the leading end portion of the preloading portion 304 is moved It is possible to avoid a state in which it is inundated to the convex portion, thereby improving the cutting performance of the cutting and harvesting machine.

Further, in the second characterizing feature of the fourth embodiment, the preloading section 304 is provided so as to be movable up and down in the front portion of the base body. A hydraulic cylinder 303 serving as a lifting mechanism for lifting and lowering the preloading section 304 and a lifting switch 321 or a lifting / lowering switch (second lifting / lowering opening), which are artificially operated, 322, and 323, respectively. The elevation switch 321 or the elevation switch 322 is operated to raise the elevation limit 304 to the elevation limit UU1 in the upward limit UU1 and the downward limit D1 to D6 set at the upward direction Control means for operating the hydraulic cylinder 303 so as to stop and lower the preload portion 304 to the lowering limits D1 to D6 by the operation of the elevation switch 321 or the descending switch 323 Control means). And a setting dial 314 as a changing means for changing the falling limits (D1 to D6) of the control means (second control means) to high and low.

The elevation switch 321 or the lowering switch 323 can be stopped by raising the elevation limit 304 to the elevation limit UU1 by operating the elevation switch 321 or the elevation switch 322, It is possible to lower the preload portion 304 to the lowering limits (D1 to D6) and stop the operation. In this case, the falling limits (D1 to D6) can be changed to high and low.

When the concavities and convexities of the farmland surface are relatively large, the lowering limits (D1 to D6) may be set to the upper side.

Thus, for example, when the turning of the bogie is completed and the preloading section 304 is lowered to the farmland surface to enter the next cutting operation, the preliminary holding section 304 is moved by the elevation switch 321 or the lowering switch 323 The height of the preloading portion 304 is secured with respect to the agricultural land so that the leading end portion of the preloading portion 304 can not reach the farming surface It is possible to avoid a state in which it projects into the convex portion. Therefore, when the turning of the bogies is completed and the preloading unit 304 is lowered to the farmland surface to enter the next cutting cycle, it is unnecessary to pay more attention to the height of the preloading unit 304 with respect to the farmland surface.

Therefore, in the ascending / descending structure of the preloading portion 304, for example, when the turning of the preloading portion 304 is finished and the preloading portion 304 is lowered to the farmland surface to enter the next cutting operation, It is possible to reduce the state of entering into the convex portion of the agricultural land, thereby improving the cutting performance of the cutting and harvesting machine.

It is further advantageous to provide the following configuration.

And the setting switch 314 is configured to be set to an operation state and a stop state. In the stop state of the setting switch 314, the falling limits (D1 to D6) of the second control means are set above the falling limit (DD1) of the first control means. When the setting switch 314 is stopped, the preload portion 304 is lowered to the lowering limits (D1 to D6) of the second control means and stopped by the operation of the elevation switch 321 or the lowering switch 323 The first control means is configured to be able to raise and lower the preload portion 304 from the down limits (D1 to D6) of the second control means to the up and down sides by the operation of the operation lever 312. [

According to this configuration, since the setting switch 314 can be set to the stopped state (state in which the falling limit DD1 exists but the falling limit DD1 can not be changed to high or low), the setting switch 314 is set to the stop state The elevation switch 321 or the descending switch 322 as the second elevating operation opening is disposed above the descending limit DD1 of the first control means (the operation lever 312 as the first elevating operation opening) 323) is set to the lower limit (D1 to D6).

When the turning of the bobbin 304 is completed and the bobbin 304 is lowered to the farmland surface to enter the next cutting operation, the elevating switch 321 or the lowering switch 323 switches the pre- The height of the preload portion 304 is secured with respect to the farmland surface by lowering the first control means (the lifting switch 321 or the lowering switch 323 as the second lifting and lowering operation port) by the lowering limits D1 to D6 State. The operation of the operation lever 312 causes the preloading section 304 to move downward by the second control means (the lifting switch 321 or the lowering switch 323 as the second lifting and lowering operation opening) It is possible to move up and down from the limits D1 to D6 so that the preloading portion 304 can be moved up and down along the farmland surface by the operation of the operation lever 312. [

Therefore, when the setting switch 314 is set to the stop state, for example, when the turn of the bogie is completed and the preloading section 304 is lowered to the farmland surface to enter the next cutoff stroke, Or the lowering switch 323 causes the preloading section 304 to descend to the lowering limits D1 to D6 of the second control means (the lifting switch 321 or the lowering switch 323 as the second lifting and lowering operation opening) , The operation of the operation lever 312 allows the preloading section 304 to move up and down along the farmland surface to smoothly shift to the cutoff stroke, thereby improving the cutting performance of the cutoff harvester.

Lastly, in order to facilitate the reference to the drawings, the corresponding claims in the drawings are inserted in the claims, but they are not intended to be limited to the embodiments showing the scope of protection of the present invention.

303: lifting mechanism
304: Example mounting
312: a lifting / lowering operation opening, a first lifting / lowering opening
314: Change means
321, 322, 323: a lifting and lowering operation opening, a second lifting and lowering opening
UU1: Lift limit
DD1: Falling limit
D1 to D6: falling limit

Claims (13)

A preloading portion 304 installed on the front portion of the base so as to be movable up and down,
A lifting mechanism 303 for lifting and lowering the preload portion 304,
And a second lift operation opening 321 (322, 323) for lifting and lowering the preloading section 304 through the lifting mechanism 303 by artificially operating the lifting / In this case,
The cut-
The lifting mechanism 303 is moved upward and downward by the operation of the first lifting and lowering operation tool 312 in the lifting range of the upper limit UU1 and the lowering limits DD1 and D1 to D6 set below, The first control means A1 for operating the elevating mechanism 303 to stop the elevating mechanism 303 by the operation of the first elevating and lowering operation means 312,
The elevation limit UU1 is set to the elevation limit UU1 by the operation of the second elevation opening 321 and the elevation limit opening 321 in the lower elevation limit U1 The elevating mechanism 303 is moved so that the elevation mechanism 304 is stopped to descend to the descending limits D1 to D6 by the operation of the second elevation operation means 321 and 322, A second control means (A2) for actuating and operating the control means
Further comprising changing means (314) for changing the falling limits (DD1, D1 to D6) of the first control means (A1) and the falling limits (D1 to D6) of the second control means (A2)
The changing means 314 is configured to be set to the operating state (D1 to D6) and the stopped state (OFF)
The lowering limits (D1 to D6) of the first control means and the lowering limits (D1 to D6) of the second control means coincide in the operating states (D1 to D6) of the changing means (314)
The lowering limits (D1 to D6) of the second control means are set above the lowering limit (DD1) of the first control means in the stop state (OFF) of the changing means (314) , Cutting harvester. A preloading portion 304 installed on the front portion of the base so as to be movable up and down,
A lifting mechanism 303 for lifting and lowering the preload portion 304,
And a second lift operation opening 321 (322, 323) for lifting and lowering the preloading section 304 through the lifting mechanism 303 by artificially operating the lifting / In this case,
The cut-
The lifting mechanism 303 is moved upward and downward by the operation of the first lifting and lowering operation tool 312 in the lifting range of the upper limit UU1 and the lowering limits DD1 and D1 to D6 set below, The first control means A1 for operating the elevating mechanism 303 to stop the elevating mechanism 303 by the operation of the first elevating and lowering operation means 312,
The elevation limit UU1 is set to the elevation limit UU1 by the operation of the second elevation opening 321 and the elevation limit opening 321 in the lower elevation limit U1 The elevating mechanism 303 is moved so that the elevation mechanism 304 is stopped to descend to the descending limits D1 to D6 by the operation of the second elevation operation means 321 and 322, A second control means (A2) for actuating and operating the control means
Further comprising changing means (314) for changing the falling limits (DD1, D1 to D6) of the first control means (A1) and the falling limits (D1 to D6) of the second control means (A2)
The changing means 314 is configured to be set to the operating state (D1 to D6) and the stopped state (OFF)
The falling limits (D1 to D6) of the second control means are set above the falling limit (DD1) of the first control means in the stop state (OFF) of the changing means (314)
The operation of the second lifting and lowering operating member 321 (322, 323) causes the preloading unit 304 to lower the falling limits D1 to D3 of the second control means in the stop state (OFF) D6 and then the elevation portion 304 is elevated and lowered from the lowering limits D1 to D6 of the second control means by the operation of the first elevation operation means 312 , Wherein the first control means is constituted. A preloading portion 304 installed on the front portion of the base so as to be movable up and down,
A lifting mechanism 303 for lifting and lowering the preload portion 304,
And a second lift operation opening 321 (322, 323) for lifting and lowering the preloading section 304 through the lifting mechanism 303 by artificially operating the lifting / In this case,
The cut-
The lifting mechanism 303 is moved upward and downward by the operation of the first lifting and lowering operation tool 312 in the lifting range of the upper limit UU1 and the lowering limits DD1 and D1 to D6 set below, The first control means A1 for operating the elevating mechanism 303 to stop the elevating mechanism 303 by the operation of the first elevating and lowering operation means 312,
The elevation limit UU1 is set to the elevation limit UU1 by the operation of the second elevation opening 321 and the elevation limit opening 321 in the lower elevation limit U1 The elevating mechanism 303 is moved so that the elevation mechanism 304 is stopped to descend to the descending limits D1 to D6 by the operation of the second elevation operation means 321 and 322, A second control means (A2) for actuating and operating the control means
Further comprising changing means (314) for changing the falling limits (DD1, D1 to D6) of the first control means (A1) and the falling limits (D1 to D6) of the second control means (A2)
The changing means 314 is configured to be set to the operating state (D1 to D6) and the stopped state (OFF)
The falling limits (D1 to D6) of the second control means are set above the falling limit (DD1) of the first control means in the stop state (OFF) of the changing means (314)
The falling limit D2 of the second control means in the stop state (OFF) of the changing means 314 is set to be substantially the same height as the farmland surface G,
The lowest position DD1 of the lowering limit of the first control means in the stop state (OFF) of the changing means 314 is lower than the agricultural land surface G, Is set to be higher than a falling limit of the elevation range. A preloading portion 304 installed on the front portion of the base so as to be movable up and down,
A lifting mechanism 303 for lifting and lowering the preload portion 304,
And a second lift operation opening 321 (322, 323) for lifting and lowering the preloading section 304 through the lifting mechanism 303 by artificially operating the lifting / In this case,
The cut-
The lifting mechanism 303 is moved upward and downward by the operation of the first lifting and lowering operation tool 312 in the lifting range of the upper limit UU1 and the lowering limits DD1 and D1 to D6 set below, The first control means A1 for operating the elevating mechanism 303 to stop the elevating mechanism 303 by the operation of the first elevating and lowering operation means 312,
The elevation limit UU1 is set to the elevation limit UU1 by the operation of the second elevation opening 321 and the elevation limit opening 321 in the lower elevation limit U1 The elevating mechanism 303 is moved so that the elevation mechanism 304 is stopped to descend to the descending limits D1 to D6 by the operation of the second elevation operation means 321 and 322, A second control means (A2) for actuating and operating the control means
Further comprising changing means (314) for changing the falling limits (DD1, D1 to D6) of the first control means (A1) and the falling limits (D1 to D6) of the second control means (A2)
The changing means 314 is configured to be set to the operating state (D1 to D6) and the stopped state (OFF)
The falling limits (D1 to D6) of the second control means are set above the falling limit (DD1) of the first control means in the stop state (OFF) of the changing means (314)
When the second elevation opening 321 (322, 323) is operated in the stop state (OFF) of the changing means 314,
Wherein the second control means comprises:
It is determined whether or not the preloading section 304 is located at the upper limit UU1 of the second control means,
If the preloading section 304 is not located at the elevation limit UU1 of the second control means, the elevating section 304 is elevated and raised to the elevation limit UU1 of the second control means To stop the preload portion 304,
When the preloading section 304 is located at the upper limit UU1 of the second control means, the preloading section 304 is operated to descend to descend to the lowering limits D1 to D6 of the second control means And stops the preloading section (304) when the preheating section (304) is stopped. The method according to claim 4, characterized in that, in the stop state (OFF) of the changing means (314)
The operation of the first lifting and lowering operation tool 312 is performed while the preheating part 304 is being lowered by the second control means on the basis of the operation of the second lifting and lowering operation tool 321 (322, 323) Wherein when the lifting mechanism (303) is actuated by the lifting mechanism (303) in the upward direction, the preloading section (304) is elevated prior to the lifting operation by the second control means. A preloading portion 304 installed on the front portion of the base so as to be movable up and down,
A lifting mechanism 303 for lifting and lowering the preload portion 304,
And a second lift operation opening 321 (322, 323) for lifting and lowering the preloading section 304 through the lifting mechanism 303 by artificially operating the lifting / In this case,
The cut-
The lifting mechanism 303 is moved upward and downward by the operation of the first lifting and lowering operation tool 312 in the lifting range of the upper limit UU1 and the lowering limits DD1 and D1 to D6 set below, The first control means A1 for operating the elevating mechanism 303 to stop the elevating mechanism 303 by the operation of the first elevating and lowering operation means 312,
The elevation limit UU1 is set to the elevation limit UU1 by the operation of the second elevation opening 321 and the elevation limit opening 321 in the lower elevation limit U1 The elevating mechanism 303 is moved so that the elevation mechanism 304 is stopped to descend to the descending limits D1 to D6 by the operation of the second elevation operation means 321 and 322, A second control means (A2) for actuating and operating the control means
Further comprising changing means (314) for changing the falling limits (DD1, D1 to D6) of the first control means (A1) and the falling limits (D1 to D6) of the second control means (A2)
The changing means 314 is configured to be set to the operating state (D1 to D6) and the stopped state (OFF)
The falling limits (D1 to D6) of the second control means are set above the falling limit (DD1) of the first control means in the stop state (OFF) of the changing means (314)
The second lifting and lowering operation ports 322 and 323 are provided with the lifting switch 322 and the lifting switch 323 provided in the gripping portion 312a of the first lifting and lowering operation tool 312,
Wherein the second control means comprises:
When the up switch 322 is operated in the stop state (OFF) of the changing means 314,
If the preloading section 304 is not located at the elevation limit UU1 of the second control means and the elevation of the preloading section 304 is raised to the elevation limit UU1 of the second control means, To stop mounting 304,
When the down switch 323 is operated in the stop state (OFF) of the changing means 314,
When the preloading section 304 is not located at the lowering limits D1 to D6 of the second control means, the lowering limits D1 to D6 , The stopping portion (304) is stopped. 7. The method according to claim 6, wherein, in the stop state (OFF) of the changing means (314)
The lift mechanism 303 is operated by the operation of the first lift mechanism 312 while the second control means is performing the lowering operation of the preload portion 304 on the basis of the operation of the lowering switch 323, , The preloading section (304) is elevated prior to the lowering operation by the second control means. A preloading portion 304 installed on the front portion of the base so as to be movable up and down,
A lifting mechanism 303 for lifting and lowering the preload portion 304,
And a second lift operation opening 321 (322, 323) for lifting and lowering the preloading section 304 through the lifting mechanism 303 by artificially operating the lifting / In this case,
The cut-
The lifting mechanism 303 is moved upward and downward by the operation of the first lifting and lowering operation tool 312 in the lifting range of the upper limit UU1 and the lowering limits DD1 and D1 to D6 set below, The first control means A1 for operating the elevating mechanism 303 to stop the elevating mechanism 303 by the operation of the first elevating and lowering operation means 312,
The elevation limit UU1 is set to the elevation limit UU1 by the operation of the second elevation opening 321 and the elevation limit opening 321 in the lower elevation limit U1 The elevating mechanism 303 is moved so that the elevation mechanism 304 is stopped to descend to the descending limits D1 to D6 by the operation of the second elevation operation means 321 and 322, A second control means (A2) for actuating and operating the control means
Further comprising changing means (314) for changing the falling limits (DD1, D1 to D6) of the first control means (A1) and the falling limits (D1 to D6) of the second control means (A2)
The changing means 314 is configured to be set to the operating state (D1 to D6) and the stopped state (OFF)
The falling limits (D1 to D6) of the second control means are set above the falling limit (DD1) of the first control means in the stop state (OFF) of the changing means (314)
When the second lifting and lowering opening 321 (322, 323) is operated in the operating state (D1 to D6) of the changing means 314,
Wherein the second control means comprises:
It is determined whether or not the preloading section 304 is located at the upper limit UU1 of the second control means,
If the preloading section 304 is not located at the upper limit UU1 of the second control means, the preliminary loading section 304 is raised and ascends to the upper limit UU1 of the second control means To stop the preload portion 304,
When the preloading section 304 is located at the upper limit UU1 of the second control means, the preloading section 304 is operated to descend to descend to the lowering limits D1 to D6 of the second control means And stops the preloading section (304) when the preheating section (304) is stopped. The method according to claim 8, wherein in the operating states (D1 to D6) of said changing means (314)
The operation of the first lifting and lowering operation tool 312 is performed while the preheating part 304 is being lowered by the second control means on the basis of the operation of the second lifting and lowering operation tool 321 (322, 323) Characterized in that when the lifting mechanism (303) is actuated by the lifting mechanism (303) in the upward direction, the preloading section (304) is elevated prior to the lifting operation by the second control means. A preloading portion 304 installed on the front portion of the base so as to be movable up and down,
A lifting mechanism 303 for lifting and lowering the preload portion 304,
And a second lift operation opening 321 (322, 323) for lifting and lowering the preloading section 304 through the lifting mechanism 303 by artificially operating the lifting / In this case,
The cut-
The lifting mechanism 303 is moved upward and downward by the operation of the first lifting and lowering operation tool 312 in the lifting range of the upper limit UU1 and the lowering limits DD1 and D1 to D6 set below, The first control means A1 for operating the elevating mechanism 303 to stop the elevating mechanism 303 by the operation of the first elevating and lowering operation means 312,
The elevation limit UU1 is set to the elevation limit UU1 by the operation of the second elevation opening 321 and the elevation limit opening 321 in the lower elevation limit U1 The elevating mechanism 303 is moved so that the elevation mechanism 304 is stopped to descend to the descending limits D1 to D6 by the operation of the second elevation operation means 321 and 322, A second control means (A2) for actuating and operating the control means
Further comprising changing means (314) for changing the falling limits (DD1, D1 to D6) of the first control means (A1) and the falling limits (D1 to D6) of the second control means (A2)
The changing means 314 is configured to be set to the operating state (D1 to D6) and the stopped state (OFF)
The falling limits (D1 to D6) of the second control means are set above the falling limit (DD1) of the first control means in the stop state (OFF) of the changing means (314)
The second lifting and lowering operation ports 322 and 323 are provided with the lifting switch 322 and the lifting switch 323 provided in the gripping portion 312a of the first lifting and lowering operation tool 312,
Wherein the second control means comprises:
When the up switch 322 is operated in the operating states D1 to D6 of the changing means 314,
If the preloading section 304 is not located at the elevation limit UU1 of the second control means and the elevation of the preloading section 304 is raised to the elevation limit UU1 of the second control means, To stop mounting 304,
When the lowering switch 323 is operated in the operating states (D1 to D6) of the changing means 314,
When the preloading section 304 is not located at the lowering limits D1 to D6 of the second control means, the lowering limits D1 to D6 , The stopping portion (304) is stopped. 11. The method according to claim 10, wherein in the operating states (D1 to D6) of said changing means (314)
The lift mechanism 303 is operated by the operation of the first lift mechanism 312 while the second control means is performing the lowering operation of the preload portion 304 on the basis of the operation of the lowering switch 323, , The preloading section (304) is elevated prior to the lowering operation by the second control means. A combine harvester comprising the cut-off harvester according to any one of claims 1 to 11. delete

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