JP2003136986A - Transmission structure for working machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve operability. SOLUTION: This transmission structure can select a working device driving state in which power is transmitted to a working device 3 and a working device stopping state in which power is not transmitted to the working device with operation of a first transmission device 46 composed of a continuously variable transmission and operation of a second transmission device changing speed of power after speed change by the first transmission device 46.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission structure for a working machine provided with a first transmission which is a continuously variable transmission and a second transmission which shifts power after shifting by the first transmission.

[0002]

2. Description of the Related Art Conventionally, in the power transmission structure for a work machine as described above, the power from the engine can be shifted to a desired traveling speed by operating the first transmission and the second transmission. By operating a separately provided work switching device, it is possible to switch between a work device driving state in which power is transmitted to the work device and a work device stopped state in which power is not transmitted to the work device. Was there.

[0003]

That is, according to the above-mentioned prior art, the working traveling state in which the work is performed at a desired traveling speed suitable for the work and the traveling traveling state in which the work is performed at the desired traveling speed without performing the work. To switch between and
Since the transmission and the second transmission must be operated and the work switching device must be operated, there is room for improvement in improving operability.

An object of the present invention is to improve operability.

[0005]

[Means for Solving the Problems] [Structure] In order to achieve the above object, in the invention according to claim 1 of the present invention, the operation of the first transmission including a continuously variable transmission and the first shift are performed. By the operation of the second transmission that shifts the power after shifting by the device, the working device driving state in which power is transmitted to the working device and the working device stopped state in which power is not transmitted to the working device are switched to appear. Configured.

[Operation] According to the invention described in claim 1, the operation of the first transmission or the second transmission is performed,
It becomes possible to easily switch between the working traveling state in which the work is performed at a desired traveling speed suitable for the work and the moving traveling state in which the work is performed at the desired traveling speed without performing the work.

Moreover, since the first transmission is a continuously variable transmission, when the first transmission is operated, it is possible to perform a smooth shifting operation with a feeling of stepless operation.
Compared with the case of a step-variable transmission, various shift states can be displayed according to the purpose, and if the second transmission is also a continuously variable transmission, the second transmission is operated. Even in this case, it is possible to perform a smooth gear shifting operation with a feeling of stepless operation, and it is possible to reveal various gear shifting states according to the purpose.

[Effect] Therefore, it is possible to improve the operability and obtain a smooth shift operation feeling.

[Structure] In the invention according to claim 2 of the present invention, in the invention according to claim 1, the second transmission is configured by a stepped transmission.

[Operation] According to the invention described in claim 2, since the second transmission is composed of a stepped transmission that is less expensive than a continuously variable transmission, the first transmission and the second transmission are The manufacturing cost can be reduced as compared with the case where both are constituted by continuously variable transmissions.

[Effect] Therefore, it is possible to improve the operability while reducing the manufacturing cost.

[Structure] In the invention according to claim 3 of the present invention, in the invention according to claim 1 or 2, in the working device driving state, the working device is normally driven regardless of forward and backward movement. As configured.

[Operation] According to the third aspect of the present invention, it is possible to prevent the occurrence of a work defect due to the work device being reversely driven as the machine body moves backward.

Further, even when the machine body is moved backward, the work device can be driven in the forward direction to continue the work.

That is, for example, when the working machine is a harvesting machine such as a combine harvester or a carrot harvesting machine, a harvesting and transporting apparatus, which is an example of the working apparatus, is used as the machine body is moved backward for alignment and the like. When it is driven in the reverse direction, a work failure such as crop clogging or crop release occurs due to the crop being conveyed being conveyed in the opposite direction. However, in the invention according to claim 11, the machine is moved backward. Even if it is done, since the harvesting and transporting device is driven in the normal direction, the crops that are being harvested and transported are not transported in the opposite direction. It becomes possible to avoid the occurrence.

Even when the machine body is moved backward, the harvesting and conveying device is driven in the normal direction, so that the crops in the middle of harvesting and conveying are threshing device (in the case of combine) and leaf cutting device (of the carrot harvester). In such a case, it is possible to carry out the following processing.

[Effect] Therefore, it is possible to prevent the occurrence of a work defect due to the work device being reversely driven with the backward movement of the machine body, and it is also possible to improve the work efficiency.

[Structure] In the invention according to claim 4 of the present invention, in the invention according to claim 1 or 2, the shift moving member mounted on the second transmission is the first shift gear.
The work device stopped state is displayed in association with the appearance of the reverse state by the operation of the transmission or the second transmission.

[Operation] According to the invention described in claim 4, even when the one-way clutch for preventing the transmission of the reverse rotation power is not provided in the transmission system for the working device, the working device is stopped when the machine body is moved backward. By doing so, it becomes possible to avoid occurrence of a work defect or damage to the work device due to the work device being driven in reverse.

Incidentally, for example, when the working machine is a harvesting working machine such as a combine harvester or a carrot harvesting machine, when the harvesting and conveying apparatus which is an example of the working apparatus is driven in reverse, the crops being conveyed are reversed. Since it will be transported to
If work defects such as crop clogging and crop release due to reverse transportation occur, and if the work machine is a transplant work machine such as a rice transplanter, seedling planting, which is an example of a work device, When the planting mechanism and the like mounted on the device is reversely driven, there is a possibility that a work failure in the seedling planting device or damage to the planting mechanism or the like may occur due to the reverse driving.

[Effects] Therefore, while simplifying the structure and reducing the manufacturing cost, occurrence of a work defect or damage to the work device due to the work device being driven in reverse when the machine body is moved backwards. You can now avoid it.

[Structure] In the invention according to claim 5 of the present invention, in the invention according to any one of claims 1 to 4, the shifting member provided in the second transmission is for shifting. The working device stop state is displayed with the appearance of the high-speed transmission state by the operation of the second transmission.

[Operation] According to the invention described in claim 5, when the machine body is driven at a high speed, the work device does not have to be provided with a high-speed check mechanism for preventing transmission of high-speed power to the power transmission system for the work device. Therefore, it is possible to prevent the occurrence of work failure and damage to the work device due to the work device being driven at high speed.

By the way, for example, when the working machine is a harvesting machine such as a combine harvester or a carrot harvesting machine, when the harvesting and conveying apparatus, which is an example of the working apparatus, is driven at high speed, the crops being conveyed and harvested at high speed. Since it will be transported, defective transport due to the high-speed transport and work defects such as crop clogging will occur, and if the working machine is a transplanting machine such as a rice transplanter, When the planting mechanism equipped in the seedling planting device, which is an example of the device, is driven at high speed,
There is a risk that defective planting or damage to the planting mechanism may occur due to the high speed driving.

[Effect] Therefore, while the structure is simplified and the manufacturing cost is reduced, the occurrence of a work defect or the damage of the work device due to the work device being driven at a high speed as the machine body travels at a high speed. You can avoid it.

[Structure] In the invention according to claim 6 of the present invention, in the invention according to any one of claims 1 to 5, the operation of the second transmission in the working device driving state. In conjunction with the above, a work speed change device for changing the drive speed of the work device to a speed according to the traveling speed after the speed change by the second speed change device is provided.

[Operation] According to the invention described in claim 6, the drive speed of the work device is set to a speed corresponding to the traveling speed after the gear shift by the second transmission, without manually operating the work transmission. It is possible to change gears, and it is possible to avoid the occurrence of work failure due to the traveling speed and the drive speed of the work device not corresponding.

Incidentally, for example, when the working machine is a harvesting machine such as a combine harvester and a carrot harvesting machine, the traveling speed and the driving speed of the harvesting and transporting apparatus, which is an example of the working apparatus, do not correspond to each other. As a result, poor transport such as insufficient transport speed for the amount of crops to be harvested and poor work such as clogging of crops will occur, and the working machine will be a transplanting machine such as a rice transplanter. In some cases, if the traveling speed and the drive speed of the seedling planting device, which is an example of a working device, do not correspond, work defects such as the planting interval of the seedlings to be planted accompanying traveling may deviate from the proper interval. Come to do.

[Effect] Therefore, while further improving the operability, it is possible to prevent the occurrence of work failure due to the disagreement between the traveling speed and the drive speed of the working device.

[Structure] According to a seventh aspect of the present invention, in the invention according to any one of the first to sixth aspects, the transmission shaft mounted on the second transmission is slid. The second transmission is configured to be shifted, and the working device driven state and the working device stopped state are switched.

[Operation] According to the invention as set forth in claim 7, it is possible to dispose a dedicated moving member for shifting the second transmission and switching the transmission state to the working device.
By the sliding operation of the transmission shaft, it becomes possible to change the speed of the second transmission and to switch between the working device driven state and the working device stopped state.

[Effect] Therefore, it is possible to improve the operability while simplifying the structure and reducing the manufacturing cost.

[Structure] In the invention according to claim 8 of the present invention, in the invention according to claim 6 above, the transmission of the second transmission is changed by sliding the transmission shaft mounted on the second transmission. The work device drive state and the work device stop state are switched, and the work transmission is shifted.

[Operation] According to the invention described in claim 8, there is no need to provide a dedicated moving member for shifting the second transmission, switching the transmission state to the working device, and shifting the working transmission. Even by the sliding operation of the transmission shaft, it is possible to change the speed of the second transmission, switch between the working device driving state and the working device stopped state, and change the speed of the working transmission.

[Effect] Therefore, it is possible to effectively improve the operability while simplifying the structure and reducing the manufacturing cost.

[Structure] In the invention according to claim 9 of the present invention, in the invention according to claim 7 or 8, the transmission shaft is a rotary shaft, and the transmission shaft is internally mounted and the peripheral surface thereof. A spring-biased ball that projects from the
From a cylindrical boss that is externally fitted to the transmission shaft so as to be integrally rotatable and relatively slidable, and a plurality of ring-shaped recesses that allow engagement of the balls are formed on a fitting surface with the transmission shaft. A ball detent mechanism that holds the transmission shaft at a desired gear shift position is configured.

[Operation] According to the invention described in claim 9, the ball detent mechanism has a small outer diameter as compared with the case of internally mounting a spring-biased ball toward the transmission shaft on the boss side. In addition, the bearing having a small diameter can be adopted as the bearing for externally fitting and supporting the boss.

Further, as compared with the case where a ball detent mechanism is formed between the transmission shaft and a fixed member such as a transmission case, the transmission shaft can be smoothly rotated with less resistance.

[Effect] Therefore, the transmission switching structure can be downsized without causing a transmission loss.

[Structure] According to a tenth aspect of the present invention, in the invention according to any one of the first to ninth aspects, the operation of the first transmission and the second transmission is performed. It is configured to be performed by moving a single operation tool.

[Operation] According to the invention described in claim 10, since only a single operation tool is provided for gear shifting, the control section is equipped with the single operation tool with good operability. To secure the space for the operation, and at the time of the gear shifting operation, by simply moving the operating tool, the gear shifting state according to the purpose is displayed, and the working device driving state and the working device stop It becomes easy to switch to the state.

[Effects] Therefore, it is possible to save the space for the operating tool and to further improve the operability.

[0043]

DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows an overall side surface of a self-removing combine as an example of a working machine, and FIG. 2 shows an overall plane thereof. The combine has a pair of left and right crawler type traveling machines. On the front left side of the traveling body 2 equipped with the device 1,
A harvesting-type harvesting and conveying device 3, which is an example of a working device, is connected to the traveling machine body 2 such that the harvesting and conveying device 3 can be moved up and down about a horizontal axis.
A control part 6 including a control tower 4 and a driver's seat 5 is formed on the front right side of the harvesting and transporting device 3 in the traveling machine body 2 and a position immediately after the control part 6 from the harvesting and transporting device 3. A threshing device 7 for performing threshing processing, sorting processing, and the like is mounted on the left side of the threshing device 7 in the traveling machine body 2, and a waste straw cutting device 8 for shredding the waste straw from the threshing device 7 is provided.
And a bag packing device 11 for packing the grains conveyed from the threshing device 7 through the lifting conveyor 9 into the grain bag 10 at the right rear portion of the threshing device 7 in the traveling machine body 2. Has been done.

As shown in FIG. 1, the left and right crawler type traveling devices 1 are provided with drive wheels 12 provided at the front thereof, idle wheels 13 provided at the rear of the crawler type traveling device 1 so as to be positionally adjustable in the front-rear direction, and those drive wheels. It is composed of three outer wheels 14 arranged between the outer ring 12 and the idler wheel 13, and a crawler belt 15 stretched so as to surround them.

As shown in FIGS. 1 and 2, the harvesting and conveying device 3 comprises three dividers 16 for scooping the laid planted culms, and left and right raising mechanisms 1 for raising the laid planted culms.
7. A clipper-shaped mowing mechanism 18 for cutting the root side of a planted grain culm such as rice and wheat, and a transport mechanism for changing the posture from a vertical orientation to a horizontal orientation while transporting the harvested grain culm backward 19 and the like are provided so as to carry out cutting and feeding of two lines.

As shown in FIGS. 3 and 4, the threshing device 7
Is the threshing processing unit 2 in which the threshing processing direction is set to the front-back direction.
0, the sorting processing section 21 in which the sorting processing direction is set to the left and right, and the collecting section 2 in which the collecting and conveying direction is set to the front and back.
2 are provided in that order from above, and the threshing device 7
In the threshing processing section 20 arranged in the upper part of the feed chain 23 arranged on the left outer side of the threshing processing section 20, by sandwiching the stock side of the harvested culm from the carrying mechanism 19 and carrying it backward, The tip side of the cut grain culm is guided on the receiving net 25 in the handling room 24 formed on the upper left side of the threshing device 7, and the handling room 2
By rotating the handling cylinder 26 installed in the front-rear direction in 4 around the support shaft 27, it is possible to perform the threshing process on the tip side of the harvested culm guided on the receiving net 25 by the feed chain 23. Is configured.

In the sorting processing section 21 provided in the upper and lower intermediate portions of the threshing device 7, the swing sorting mechanism 28 provided below the receiving net 25 swings in the left and right direction by the rotation of the drive shaft 29 facing forward and backward. By being driven dynamically, the threshing-treated product leaking from the receiving net 25 along with the threshing treatment and the threshing-treated product discharged from the dust-sending port 30 formed at the lower end of the handling chamber 24 in the threshing-processing direction are ,
In the lower left of the handling cylinder 26, a sieving and sorting process is performed in which the sieving process is performed by sieving into grain, straw scraps, and broken straws, etc., while transferring to the right side, which is the lower side of the sorting process direction. The threshing device 7 which is arranged in the left-right direction rotates around the support shaft 32 to generate a sorting wind, and the sorting wind is located on the lower side in the sorting processing direction from the Karaji 31.
Sorting air passage 3 extending to the dust outlet 33 formed at the right end of the
By making the inside 4 flow, the threshing-treated product supplied into the sorting air passage 34 is configured to be subjected to a wind sorting process in which the threshing-treated product is blown into grains, straw scraps, broken straws, and the like due to a difference in specific gravity. .

A collecting section 22 provided below the threshing device 7.
Is arranged on the upper side in the sorting processing direction of the swing sorting mechanism 28 by rotating the No. 1 screw 35 disposed below the swing sorting mechanism 28 in the sorting processing direction around the support shaft 36. The grain that has leaked from the Glen sieve 37 that has passed through and has passed through the sorting air passage 34 is conveyed as the first grain toward the lifting conveyor 9, and is also below the swing sorting mechanism 28 in the sorting processing direction. The No. 2 screw 38 disposed on the shaft rotates around the support shaft 39, so that the No. 2 screw leaks from the Straw rack 40 disposed on the lower side in the sorting processing direction of the swing sorting mechanism 28, and the sorting air passage is provided. The mixture of grains and straw scraps that have passed through 34 is conveyed as a second product toward the reduction-type reducing and conveying mechanism 41, and the lower blade 42 of the reducing and conveying mechanism 41 rotates integrally with the second screw 38. And the second one is the handling room It is configured to reprocessed reduced to 4.

Among the threshed products, cut straws transferred from the Straw rack 40 of the rocking / sorting mechanism 28 to the rear end of the rocking / sorting mechanism 28 without leaking, and riding on the sorting wind, the lower side in the sorting / processing direction. Dust such as straw dust blown up toward the upper part is discharged to the outside of the machine through the dust discharge port 33 as a third item.

Although not shown in the drawings, the so-called discharge straw cutting device 8 is so-called that the discharge straw conveyed by the feed chain 23 in the left-right direction is folded in two in a pine needle shape and shredded in order from the bent end. Cylinder type cutter is adopted, so that compared to the case of adopting a disc type cutter that receives the discharged straw in the left-right direction as it is and shreds into a plurality of discs, the discharged straw is cut behind the threshing device 7. The lateral length of the installation space required for the installation of the device 8 can be significantly reduced, and as a result, the installation space for the bagging device 11 can be secured on the right side thereof.

As shown in FIGS. 1 and 2, the bag filling device 1
1 uses a two-bag type in which the grains conveyed by the lifting conveyor 9 are guided and supplied into the left and right grain bags 10 through the left and right bifurcated discharge tubes 43. The bag packing work efficiency can be improved as compared with the case of using the formula type.

That is, right behind the harvesting and conveying device 3 and the control section 6 which are juxtaposed in the left-right direction, swing selection having a length longer than that of the handling cylinder 26 so that the threshing processing direction and the selection processing direction are orthogonal to each other. A threshing device 7 whose front-rear length is significantly shortened by arranging the mechanism 28 in the left-right direction is arranged, and a space-saving waste straw cutting device 8 is provided immediately after the threshing device 7.
Two-bag type bagging device 11 capable of improving bagging work efficiency
By arranging and in parallel in the left-right direction, the swing selection mechanism 28 is arranged in the front-rear direction without decreasing the working capacity, and the front-rear length is increased. As compared with the case where the discharge straw cutting device 8 and the bag filling device 11 are arranged side by side in the front-rear direction, the front-rear length of the traveling machine body 2 on which they are mounted can be shortened and the weight can be reduced. As a result, it is possible to effectively reduce the size and weight of the combine as a whole, and it is possible to load the cargo on the bed of a light truck, even though it is a passenger type equipped with the control section 6, and thus the road conditions, etc. Therefore, even in a field such as a mountain area where a combine truck can be transported only by a light truck, a passenger combine harvester having a high working capacity can be used.

As shown in FIG. 1, FIG. 2 and FIG. 4, an engine 44 is mounted below the driver's seat 5, and the power from the engine 44 is used as a belt tension type main clutch 4.
5 to a hydrostatic stepless transmission 46, which is an example of a first transmission, and to a threshing device 7 via a belt type transmission mechanism 47 that also serves as a work clutch, and a belt tension type lifting clutch. Harvesting and conveying device 3 via 48
It is configured to be transmitted to a screw feed type elevating device 49 that elevates and lowers.

As shown in FIGS. 4 to 6, the lifting device 49 is
The power from the engine 44 is transmitted to the screw shaft 50 mounted on the traveling machine body 2 side via the lifting clutch 48, and the screw shaft 50 is normally rotated by the power, and the cylindrical shape mounted on the harvesting and conveying device 3 side. By screwing the female screw member 51 of the above to the harvesting and conveying device 3 side, the harvesting and conveying device 3 is raised, and the power transmission from the engine 44 to the screw shaft 50 is cut off by the lifting clutch 48. In this state, the braking arm 53 brakes the output pulley 52 of the lifting clutch 48 and the rotation of the screw shaft 50 is blocked, so that the harvesting and conveying device 3 is stopped at the desired height position. Further, in a state where the transmission of power from the engine 44 to the screw shaft 50 is interrupted by the lifting clutch 48, the braking action of the braking arm 53 on the output pulley 52 is released,
The screw shaft 50 is reversely rotated by the weight of the harvesting / conveying device 3 and the female screw member 51 is screw-fed to the traveling machine body 2 side to lower the harvesting / conveying device 3.

The lead angles of the screw shaft 50 and the female screw member 51 are set to a large angle at which the screw shaft 50 can be reversed by the weight of the harvesting and conveying device 3.

The up-and-down clutch 48 is urged to return to the cut-off state in which the transmission of power from the engine 44 to the screw shaft 50 is cut off by the first spring 55 that is laid across the traveling machine body 2 and the tension arm 54. .

The braking arm 53 is provided from the lower side in the direction of rotation when the output pulley 52 reversely rotates due to the weight of the harvesting and conveying device 3.
The output pulley 52 is joined to the output pulley 52 by a second spring 56 that extends across the traveling machine body 2 and the braking arm 53 so that the rotation allows the output pulley 52 to come into contact with the output pulley 52 in a stretched posture. Being energized.

The traveling machine body 2 is provided with a linking arm 58 which is erected over the linking pin 57 mounted on the harvesting and transporting device 3 and the tension arm 54 of the lifting clutch 48 so as to be swingable around its support shaft 59. The linkage arm 58 operates the tension arm 54 in conjunction with reaching the upper limit position of the harvesting and transporting device 3 to move the lifting clutch 4
8 is switched from the transmission state to the cutoff state.

That is, as the harvesting / transporting device 3 reaches the upper limit position, the raising of the harvesting / transporting device 3 can be automatically stopped.

As shown in FIGS. 7 to 11, the power transmitted to the hydrostatic continuously variable transmission 46 is transmitted to the mission case 60.
It is transmitted to the corresponding crawler type traveling device 1 via a gear type transmission 61, which is an example of a mesh type stepped transmission provided inside, and left and right side clutch brakes 62, and a gear type transmission. It is configured to be transmitted to the harvesting and conveying device 3 via a transmission device 61 and a harvesting clutch 63 which is an example of a work clutch.

The gear type transmission 61 is a second type which shifts the power after shifting by the hydrostatic stepless transmission 46 into two high and low stages.
It is configured to function as a transmission.

The structure of the gear type transmission device 61 will be described in detail. The gear type transmission device 61 is the hydrostatic stepless transmission device 4.
The low-speed first drive gear 66 and the high-speed second drive gear 67 rotate integrally with the transmission shaft 65 to which the power after shifting by 6 is transmitted via the bevel gear 64, and The ball detent mechanism 68 is provided so as to slide integrally along the axis, and the transmission shaft 6 is provided by the ball detent mechanism 68.
5 is configured so that it can be switched and held between a low speed forward position for work (see FIGS. 7 to 9), a high speed forward position for movement (see FIG. 10), and a low speed reverse position for movement (see FIG. 11). ing.

As shown in FIGS. 7 to 9, in the working low speed forward position, the first drive gear 66 is at a low speed in the traveling relay gear 70 in which the first drive gear 66 is loosely fitted to the support shafts 69 of the left and right side clutch brakes 62. And a work output gear 73 that is equipped to rotate integrally with the work output shaft 72, and the second drive gear 67 is a relay gear 70 for traveling. The engagement with the second driven gear portion 74 for high speed is released.

As shown in FIG. 10, in the high speed forward position for movement, the first drive gear 66 releases the mesh with the low speed first driven gear portion 71 and the work output gear 73, and the second
The drive gear 67 is adapted to mesh with the second driven gear portion 74 for high speed.

As shown in FIG. 11, in the moving low speed reverse position, the first drive gear 66 meshes with the low speed first driven gear portion 71 while releasing the meshing with the working output gear 73. Then, the second drive gear 67 releases the mesh with the second driven gear portion 74 for high speed.

That is, the transmission shaft 65 configured to function as a moving member does not need to be provided with a dedicated moving member for changing the speed of the gear type speed change device 61 and switching the transmission state with respect to the harvesting and conveying device 3. By the sliding operation, the gear type transmission device 61 can be shifted and the harvesting and conveying device 3 can be switched between a driven state and a stopped state. Therefore, operability can be achieved while simplifying the structure and reducing the manufacturing cost. Can be improved.

As shown in FIGS. 8 to 11, the ball detent mechanism 68 is incorporated in the transmission shaft 65 and is integrated with the transmission shaft 65 with a ball 76 urged by a spring 75 so as to project from the peripheral surface thereof. It is fitted so as to be rotatable and relatively slidable, and has a ball 76 on its fitting surface with the transmission shaft 65.
It is configured to hold the transmission shaft 65 at a desired gear shift position by the tubular boss 78 in which three ring-shaped recesses 77 are formed to allow the engagement of the transmission shaft 65. The ball detent mechanism 68 can be configured to have a small outer diameter and a compact size, and the boss 78 can be fitted and supported as compared with the case where the ball 76 biased by the spring 75 toward the transmission shaft 65 is installed. A bearing having a small diameter can be used as the bearing 79 for the transmission shaft 6. Further, as compared with a case where the ball detent mechanism 68 is formed between the transmission shaft 65 and the transmission case 60, the transmission shaft 6
5 can be rotated smoothly with little resistance.

As shown in FIGS. 7 and 9 to 11, each of the left and right side clutch brakes 62 includes a movable member 80 loosely fitted on a support shaft 69 so as to be relatively slidable, and a meshing transmission portion 81 thereof.
Is engaged with the internal fitting transmission portion 82 of the relay gear 70, while the locking portion 83 is slid to a transmission position where the locking with the locking pin 84 mounted on the mission case 60 is released. A transmission state (see FIGS. 7 and 9) in which the power after shifting by the gear type transmission device 61 is transmitted to the corresponding crawler type traveling device 1 via the transmission gear 85 meshed with the meshing transmission portion 81 and the like appears. Further, the meshing transmission portion 81 of the movable member 80 is disengaged from the internal fitting transmission portion 82 of the relay gear 70, and the locking portion 83 is locked to the locking pin 84 of the mission case 60. By performing a sliding operation to the non-transmission position for releasing the power transmission, the shut-off state (see the side clutch brake 62 on the right side in FIG. 10) in which the power after shifting by the gear type transmission device 61 is not transmitted to the corresponding crawler type traveling device 1 is set. Appearance Further, the meshing transmission portion 81 of the movable member 80 is disengaged from the internal fitting transmission portion 82 of the relay gear 70, while the engagement portion 83 thereof is engaged with the engagement pin 84 of the mission case 60. By sliding operation to the braking position, the braking state in which the corresponding crawler type traveling device 1 is stopped by braking (see the side clutch brake 62 on the right side in FIG. 11) appears.

As shown in FIGS. 1, 2, 5-7 and 12-16, the control tower 4 is capable of cross-oscillating around a horizontal support shaft 86 and a front-back support shaft 87. The steering lever 88 is configured to be linked to the lifting device 49 via the first linkage mechanism 89, and linked to the left and right side clutch brakes 62 via the second linkage mechanism 90. Has been done.

The first linkage mechanism 89 is a first balance arm 91 which is integrally pivoted around the steering lever 88 and a support shaft 86 which is oriented in the left-right direction. The first balance arm 91 extends in the front-rear direction, and the first balance arm extends from the rear end of the first balance arm 91 to the braking arm 53. The linking wire 92 and the second end extending from the front end of the first balance arm 91 to the tension arm 54.
The linkage wire 93 or the like allows the braking lever 53 to be brought into contact with the output pulley 52 by the urging of the second spring 56 in conjunction with the operation of the steering lever 88 to the neutral position in the front-rear center. The swinging operation of the tension arm 54 to the blocking position by the bias of the spring 55 is allowed, and the second operation is performed in conjunction with the operation of the control lever 88 to the front lower position.
The braking arm 53 is connected to the output pulley 5 against the bias of the spring 56.
2, and conversely, the tension arm 54 is swingably operated to the transmission position against the bias of the first spring 55 in conjunction with the operation of the steering lever 88 to the rearward rising position. ing.

The second linkage mechanism 90 includes a steering lever 88 and a second balance arm 94 in the left-right direction that swings integrally around a support shaft 87 in the front-rear direction, and the corresponding operation arm 95 of the side clutch brake 62 and the support shaft 96. The left and right crank arms 97 swinging integrally with each other, and the third left and right arms extending from the left and right ends of the second balance arm 94 to the corresponding crank arms 97.
The linkage wire 98, etc., is interlocked with the operation of the control lever 88 to the neutral position in the center of the left and right, and allows the transmission state of the left and right side clutch brakes 62 by the biasing of the spring 99 to appear. Interlocking with the operation from the neutral position of the lever 88 to either the left or right gentle turning position, the corresponding disconnection state of the side clutch brake 62 is displayed against the bias of the spring 99, and the left and right of the control lever 88 are further exposed. The side clutch brake 6 corresponding to the operation of any one of the gentle turning position to the sharp turning position against the bias of the spring 99.
It is configured to exhibit the braking state of 2.

That is, when the control lever 88 is operated to the neutral position, the harvesting and conveying device 3 can be stopped up and down, and at the same time, the left and right crawler type traveling devices 1 can be brought into a straight traveling state in which they are driven at a constant speed. Further, when the control lever 88 is operated to the front lower position, the harvesting and conveying device 3 can be lowered by its own weight, and conversely, when the control lever 88 is operated to the rearward raising position, the harvesting and conveying device is powered by the engine 44. 3 can be raised, while the control lever 8
When 8 is operated to either the left or right gentle turning position, one crawler type traveling apparatus 1 corresponding to the operation direction is allowed to idle and a slow turning state in which the other crawler type traveling apparatus 1 is driven can be revealed. Yes, the control lever 88
When one of the left and right steered turning positions is operated, one of the crawler type traveling devices 1 corresponding to the operating direction is braked and the other crawler type traveling device 1 is driven, so that a sudden turning state can be revealed. It has become.

As shown in FIGS. 12 to 15 and 17, the front-rear supporting shaft 87 is bent and formed so that its rear end portion is directed leftward, and its rear end is loosely fitted to the left-right supporting shaft 86. It is clamped by a pair of upper and lower clamping members 101 which are clamped and urged by the clamping spring 100, and the clamping action allows the control lever 88 to return to the neutral position in the front-rear direction and the left-right direction. .

That is, it is not necessary to provide a dedicated return mechanism for returning the control lever 88 to the neutral position in the front-rear direction and a dedicated return mechanism for returning the neutral position in the left-right direction. It is possible to simplify and reduce the manufacturing cost.

As shown in FIGS. 7, 16 and 18 to 20, the left and right side clutch brakes 62 include a left and right crank arm 97 that swings integrally with the operation arm 95 and a support shaft 96, and a third linkage mechanism. Control unit 6 via 102 and
It is linked to the operation pedal 103 provided in the.

The third linkage mechanism 102 includes an operation pedal 103.
A support shaft 104 that swings to support the support shaft 105, a balance arm 105 that supports the right support shaft 96 so as to swing, and
A linking spring 106 provided over the spindle 104 and the balance arm 105 causes the linking pin 107 provided on the balance arm 105 to press the left and right crank arms 97 as the operation pedal 103 is depressed. The left and right side clutch brakes 62 are configured to be in a disengaged state and a braking state.

The control portion 6 is engaged with the engaging pin 108 provided on the operation pedal 103 so that the operation pedal 103 can be operated.
A lock lever 109 is provided for maintaining the left and right side clutch brakes 62 in a braking state by holding the lever in the depressed position.

That is, the left and right side clutch brakes 6
2 is configured to be used as a traveling brake and a parking brake, so that the configuration can be simplified and the manufacturing cost can be reduced as compared with the case where the traveling brake and the parking brake are equipped. Further, there is an advantage that a state in which the harvesting and conveying device 3 is driven at a constant speed can be revealed while the traveling of the machine is stopped by a simple operation of depressing the operation pedal 103. Moreover, in the braking state, since the transmission to the left and right crawler type traveling devices 1 is cut off, the hydrostatic continuously variable transmission 46.
It is possible to avoid the inconvenience that the left and right side clutch brakes 62 interfere with each other. Therefore, as shown in FIG. 21, even if the left and right side clutch brakes 62 equipped with the friction brakes 110 are adopted, the hydrostatic It is possible to prevent the seizure of the brake disc due to the interference between the type continuously variable transmission 46 and the left and right side clutch brakes 62.

As shown in FIGS. 7, 16, 18, and 19, the left and right side clutch brakes 62 include a left and right crank arm 97 that swings integrally with the operation arm 95 and a support shaft 96, and a fourth linkage mechanism. 111, and is linked to an operation lever 113 supported by the operation pedal 103 so as to be integrally swingable around the support shaft 104 and relatively swingable around a vertically oriented support shaft 112.

The fourth linkage mechanism 111 includes an operating lever 113.
And a balance arm 114 that integrally swings around the support shaft 112,
The corresponding crank arm 9 from both ends of the balance arm 114
7, the side clutch brake 62 corresponding to the operating direction in accordance with the operating position is linked with the swinging operation of the operating lever 113 in the left-right direction. It is configured to switch to a state.

In other words, the operating lever 1 can be operated even from the exit position.
By swinging 13 in the left-right direction, the left and right crawler type traveling devices 1 are driven at a constant speed, and either one of the left and right crawler type traveling devices 1 is idled and the other crawler type traveling device 1 is idled. It is possible to switch between a gentle turning state in which the crawler type traveling device 1 is driven and a sudden turning state in which the other crawler type traveling device 1 is driven while the other crawler type traveling device 1 is driven. By swinging up and down,
It is possible to switch between a cut-off state in which the transmission to the left and right crawler type traveling devices 1 is cut off and a braking state in which the left and right crawler type traveling devices 1 are braked by switching.

By the way, the operating lever 113 is constructed so that it can be expanded and contracted, and the operating lever 113 is connected to the connecting wire 116.
By extending the spring 117, which is contracted and held via the spring, against the urging force, it is possible to facilitate the above-described switching operation from the dismount position. Note that FIG.
Reference numeral 118 shown in FIGS. 20 to 20 is a lock fitting that prevents the operation lever 113 from swinging relative to the operation pedal 103 by engaging with the operation lever 113.

As shown in FIGS. 22 to 26, a support frame 120 is installed from the mission case 60 to the side panel 119 of the control section 6, and the support frame 1 is provided.
20 is equipped with a swing bracket 123 supported by a cylindrical boss portion 122 fitted in the round hole 121 so as to swing back and forth. The swing bracket 123 includes:
A gear shift lever 125 supported by the support shaft 124 so as to be integrally swingable in the front-rear direction and relatively swingable around the support shaft 124 is provided as an example of an operating tool.

As shown in FIGS. 7, 8 and 22 to 26, the swing bracket 123 is linked to the operation arm 127 of the hydrostatic continuously variable transmission 46 via the link link 126, and the shift lever 125 is connected to the shift lever 125. The gear-type transmission 61 is provided via a linkage rod 128 passing through the center of the boss portion 122 of the swing bracket 123, and a linkage arm 130 supported by the mission case 60 so as to swing left and right around a support shaft 129.
Is linked to the transmission shaft 65 of the.

That is, the single shifting lever 125 can be operated to perform the continuously variable shifting operation of the hydrostatic continuously variable transmission 46 and the stepwise shifting operation of the gear type transmission 61. As compared with the case where a dedicated gear shift lever is provided, it is possible to save space at the location where the gear shift lever is provided and to improve gear shift operability.

Further, the speed change lever 125 and the gear type speed change device 6
Since the linkage rod 128 that links 1 and 1 comes to pass through the swing center of the shift lever 125 when shifting the hydrostatic continuously variable transmission 46, the gear type transmission 61 can be shifted. The left / right swinging operation of the shift lever 125 can be performed without being affected by the swinging operation of the shift lever 125 in the front / rear direction for shifting the hydrostatic continuously variable transmission 46. .

As shown in FIG. 27, the shift lever 125
As the movement operation path 131, two forward and downward forward speed change operation paths 132 and 133 having different gear ratios arranged in the left and right in a state of going from the neutral position to the front side of the machine body, and a reverse speed change operation from the neutral position to the rear side of the machine body. In addition to having a path 134 and a left-right selection operation path 135 that enables selection of each of the shift operation paths 132 to 134,
The guide groove 136 formed in the side panel 119 is configured to be operated and guided.

By moving the speed change lever 125 in the left-right direction along the selection operation path 135, the position of the transmission shaft 65 in the gear type speed change device 61 is set to the low speed forward position, the high speed forward position, and the low speed reverse position. It becomes possible to perform a forward / reverse switching operation and a gear ratio switching operation, which are performed by the switching operation.
In a state where 5 is located in the forward gear shift operation path 132 having a large gear ratio, the transmission shaft 65 of the gear type transmission 61 is located in the high speed forward position, and thus the gear shift lever 125 is moved in the front-rear direction. As a result, it is possible to perform stepless speed change operation in a relatively wide speed change range from zero speed to a relatively high forward limit speed that can be expressed in the operation path 132. Further, when the speed change lever 125 is positioned on the forward speed change operation path 133 having a small speed ratio, the transmission shaft 65 of the gear type speed change device 61 comes to be positioned at the low speed forward speed position, so that the speed change lever 125 is moved forward and backward. By moving in the direction, a relatively precise stepless speed change operation can be performed in a relatively narrow low speed side speed change range from zero speed to a relatively low forward limit speed that can be expressed in the operation path 133. Like Further, when the speed change lever 125 is positioned in the reverse speed change operation path 134, the gear type transmission 6
The transmission shaft 65 of No. 1 is located at the low speed reverse position,
Therefore, by moving the speed change lever 125 in the front-rear direction, it is possible to perform a stepless speed change operation from zero speed to the reverse limit speed.

That is, the forward / backward switching, the gear ratio switching, and the gear shifting in each of the gear shifting operation paths 132 to 134 are performed by the movement operating path 1 of the single gear shift lever 125.
A series of movement operations along 31 can be performed smoothly.

As shown in FIGS. 7 to 11 and FIG. 27, the shift lever 125 is set to the forward shift operation path 133 having a small gear ratio.
And the transmission shaft 65 of the gear type transmission 61 is located at the low speed forward position (see FIGS. 7 to 9), the transmission to the harvesting and conveying device 3 is performed, and the transmission lever 125 is changed to the gear ratio. When the transmission shaft 65 of the gear type transmission 61 is located at the high speed forward position by positioning it on the large forward speed shift operation path 132 (see FIG. 10), and the speed change lever 125 is positioned at the reverse speed change operation path 134. In the state where the transmission shaft 65 of the gear type transmission 61 is located at the low speed reverse position (see FIG. 11), the transmission to the harvesting and conveying device 3 is cut off.

That is, in the moving operation path 131 of the speed change lever 125, the forward speed change operation path 13 having a small speed change ratio.
3 is a working device drive area 137 for transmitting power to the harvesting and conveying device 3, and a forward gear changing operating route 132, a reverse gear changing operating route 134, and a selection operating route 135 having a large gear ratio are the harvesting and conveying device 3. Since it is the work device stop region 138 that does not transmit power to the single gearshift lever 12,
By the moving operation of No. 5, not only the shifting operation of the hydrostatic stepless transmission 46 and the gear type transmission 61 but also the state of transmitting power to the harvesting and transporting device 3 according to the shift state at that time and the harvesting and transporting device. It is possible to switch between the state in which power is not transmitted to the No. 3 and to appear.

Moreover, with the above configuration, even if the transmission system for the harvesting and conveying device 3 is not equipped with a one-way clutch that blocks the transmission of reverse power, the harvesting and conveying device 3 can be stopped when the aircraft is moved backward. Even if the transmission system for the harvesting and transporting device 3 is not equipped with a high-speed check mechanism that blocks the transmission of high-speed power, the harvesting and transporting device 3 can be stopped when the aircraft is advanced at high speed. As a result, it is possible to prevent occurrence of work failure due to the reverse operation of the harvesting and conveying device 3 and the high speed operation thereof.

As shown in FIGS. 2 and 27, in the movement operation path 131 of the speed change lever 125, the forward speed change operation path 133 having a small gear ratio, which is frequently used because it becomes the work apparatus drive region 137, is a work apparatus. Stop area 138
As a result, it is set at a position farther from the driver's seat 5 and closer to the reverse gear shift operation path 134 than the forward gear shift operation path 132 having a large gear ratio that is less frequently used.

As a result, the operation of moving the speed change lever 125 along the forward speed change operation path 133 having a small speed change ratio during work traveling, which is frequently used, is cramped even with a small model having a narrow control section 6. It is possible to perform comfortably without learning, and it is easy to perform an adjusting operation for frequently moving the speed change lever 125 over the forward speed change operation path 133 and the reverse speed change operation path 134 having a small gear ratio during work traveling.

As shown in FIGS. 7 to 11 and 27, the selection operation path 135 is the forward shift operation path 1 having a large gear ratio.
The gear ratio selector 139 extending from 32 to the forward gear shift operation path 133 having a large gear ratio is located in the fine speed forward region on the forward side of the neutral position. Thus, when the gear ratio is switched by the movement operation of the gear ratio selecting portion 139 of the gear shift lever 125, the first drive gear 66 and the second drive gear 67, which are the meshing members on the upstream side in the transmission direction, are always rotated. Therefore, it becomes possible to smoothly switch the gear ratio, and as a result, the gear ratio selecting unit 139
Is likely to occur when the first drive gear 66 and the second drive gear 67 are set to a neutral position where they stop, or the first drive gear 66, the first driven gear portion 71, and the output gear 73, or
It is possible to prevent incomplete engagement due to the fact that the second drive gear 67 and the second driven gear portion 74 have stopped rotating in a state in which they cannot mesh with each other.

In the selection operation path 135, a forward speed change operation path 133 and a reverse speed change operation path 134 having a small gear ratio.
The forward / reverse selection unit 140 spans the transmission ratio selection unit 139.
It has a selection regulation path portion 141 that regulates the movement of the speed change lever 125 to the forward speed change operation path 132 having a large speed change ratio by being located on the forward side. When the gear shift lever 125 is moved so as to pass through the selection regulation path portion 141 when the gear shift lever 125 is moved over the forward gear shift operation path 133 and the reverse gear shift operation path 134, the gear shift lever 125 has a large gear ratio. It is possible to effectively prevent an erroneous operation of moving to the operation path 132.

Further, when the backward movement state is switched to the low-speed forward movement state for work by moving the shift lever 125 on the selection regulation path portion 141, the first drive gear, which is the meshing member on the transmission direction upper side, is selected. Since the 66 always rotates and the meshing with the output gear 73 can be smoothly performed, the gear shift lever 125 is moved at the neutral position where the first drive gear 66 is stopped, so that the work gear can be operated from the reverse state. It is possible to obviate a mesh failure that may occur when switching to the low speed forward drive state and that is caused by the rotation stoppage of the first drive gear 66 and the output gear 73 in a state where they cannot mesh with each other. There is.

As shown in FIGS. 2 and 22, a threshing clutch, which is an example of a clutch lever for operating the belt type transmission mechanism 47 which also serves as a working clutch, is provided behind the forward gear shift operation paths 132 and 133 in the side panel 119. When the lever 142 and the mowing clutch lever 143, which is an example of a clutch lever for operating the mowing clutch 63, are tilted and swung to the forward entry position, their grips 144 and 145 are operated in reverse gear. It is arranged so as to be located on the right side of the path 134.

That is, the threshing clutch lever 142 and the reaping clutch lever 14 are effectively utilized by making use of the rear portions of the two forward gear shift operation paths 132 and 133 which are relatively large spaces.
Since the gear shift lever 125 and the clutch levers 142 and 143 can be compactly arranged by arranging the gears 3 and 3 in a rational manner, it is possible to reduce the space for the positions where they are arranged. Clutch levers 142, 14
When the grip portions 144 and 145 are operated to the engaged position located on the right side of the reverse gear shift operation path 134, 3 will fall forward, so that both clutch levers 142 and 143 are engaged. Even in the state in which the shift lever 125 is positioned at, the moving operation on the reverse shift operation path 134 of the shift lever 125 can be easily performed.

As shown in FIGS. 22 to 25, 28 and 29, the support frame 120 is provided with a speed change lever 125.
In the fine speed region of each gear shift operation path 132 to 134, the neutral return mechanism 146 returns to the neutral position which is the zero speed position, and in the gear shift region on the higher speed side than the fine speed region of each gear shift operation path 132 to 134. A holding mechanism 147 for holding in a desired operation position is provided.

The holding mechanism 147 is moved to the anti-support frame 120 side by the support pin 148 extending from the support frame 120 serving as a fixing member, by the engagement pin 149 provided at the end portion of the anti-support frame 120 side. The cylindrical movable body 150 is fitted onto the movable body 150 such that the movable body 150 is relatively slidable and relatively rotatable, and the movable body 150 has a ring-shaped pressing member 151, a bowl-shaped moving member 152, and a ring-shaped moving member 152. By providing the first spring 154 that presses the swing bracket 123 that integrally swings in the front-rear direction with the speed change lever 125 via the contact member 153 of the first spring 154, the speed change lever 125 can hold friction. (See FIG. 23 and FIG. 28).

The neutral return mechanism 146 is provided with the first ring member 155 for restricting the movement of the pressing member 151 toward the support frame 120 side on the movable body 150 and is movable with the second ring member 156 locked to the support shaft 148. A second spring 157 for biasing the movable body 150 in a direction away from the support frame 120 is interposed between the movable body 150 and the body 150, and an engagement pin 149 is engaged with an end surface of the movable body 150 on the side opposite to the support frame 120. V groove 158 is formed to allow the engagement pin 149
The movable body 14 is provided via the operation arm 159 and the link link 160 so that the state of being located at the bottom of the 58 is the zero speed position.
9 is linked to the swing bracket 123, the bias of the second spring 157 and the V-shaped groove 15 are increased in the very low speed state (see FIG. 29) in which the center of the engagement pin 149 is located within the groove width of the V-shaped groove 158.
The guide action of No. 8 enables the return operation of the shift lever 125 to the zero speed position (see FIG. 29).

In other words, the hydrostatic stepless transmission 46 cannot be maintained in the fine speed state, which makes it impossible to maintain the harvesting and conveying device 3 in the fine speed drive state. It is possible to avoid the occurrence of a work defect such as a mowing defect caused by maintaining the transport device 3 in a slow drive state.

Further, the holding mechanism 147 is the neutral return mechanism 146.
Since it is configured to have the above, it is possible to simplify the structure and reduce the manufacturing cost as compared with the case where they are individually configured.

22 to 25, the reference numeral 161 indicates the support shaft 148 of the holding mechanism 147 and the support frame 120.
1 for preventing the swinging bracket 123 from coming off from the
In order to allow the swinging bracket 123 to swing back and forth relative to the swinging bracket 123, the swinging bracket 123 has its boss portion 1
22 is a pair of upper and lower arc-shaped elongated holes formed with the center of 22 as a fulcrum.

Further, the reference numeral 163 shown in FIG.
The swing operation from the neutral position to the front of the control lever 88 is prevented by being operated to a position in which the control lever 88 comes into contact with the support shaft 87 in the front-rear direction that supports the control lever 88 so as to swing in the left-right direction from above. Then, it is a lowering prevention metal fitting for preventing the lowering operation of the harvesting and conveying device 3, and by this lowering prevention metal fitting, it is possible to avoid the inconvenience of the harvesting and conveying device 3 being lowered unexpectedly due to an erroneous operation of the control lever 88. There is.

As shown in FIG. 30, each outer wheel 14 in the left and right crawler type traveling devices 1 is projected from the crawler belt 15 to the left and right intermediate portions by a spatula drawing process in order to simplify the structure. It is formed in a shape having a circumferential groove 165 that allows the core metal protrusion 164 to be engaged.

[Other Embodiments] Other embodiments of the present invention will be listed below. (1) As the working machine, even a carrot harvester or a radish harvester equipped with the digging-type harvesting and conveying apparatus 3 as the working apparatus 3 or a rice transplanter equipped with the seedling planting apparatus as the working apparatus 3 Good.

(2) The first speed change device 46 allows stepless speed change by contacting the end surface of one disk with the peripheral surface of the other disk and sliding the other disk with respect to the one disk. A disc type continuously variable transmission configured as described above or a belt type continuously variable transmission may be used.

(3) The second transmission 61 is a continuously variable transmission such as a hydrostatic type or a belt type, or a stepped transmission such as a claw clutch type or a hydraulic clutch type. It may be one.

(4) Operation tool 12 dedicated to the first transmission 46
5 and the operation tool 125 dedicated to the second transmission 61 may be provided.

(5) As shown in FIG. 31, when the second speed change device 61 is in the low speed forward state, the low speed first drive gear 66 rotating integrally with the transmission shaft 65 causes the left and right side clutch brakes 62 to support shafts. A relay gear 70 for traveling, which is loosely fitted in 69.
Low speed first driven gear portion 71 and the first output gear 166 for low speed work that rotates integrally with the output shaft 72 for work.
In addition, in the high speed forward state, the second drive gear 67 for high speed that rotates integrally with the transmission shaft 65 meshes with the second driven gear portion 74 for high speed in the relay gear 70 for traveling, and Third for high-speed work that rotates integrally with the transmission shaft 65
The drive gear 167 meshes with the second output gear 168 for high-speed work that rotates integrally with the output shaft 72 for work, and further, in the reverse drive state, the first drive gear 66 changes the first driven gear portion 71 for low speed. First output gear 16 for low speed work while meshing with
6 is released, and the first drive gear 6 is released.
6, from the first output gear 166, the third drive gear 167, and the second output gear 168, the drive speed of the work device 3 is set to the second speed in association with the operation of the second transmission 61 in the work device drive state. It may be configured to have a work transmission 169 that shifts to a speed according to the traveling speed after shifting by the transmission 61.

(6) The second transmission 61 may be configured such that the reverse drive state is the working device drive state. In addition, in this configuration, the work device 3 may be configured to be normally driven even in the reverse drive state.

[Brief description of drawings]

1] Overall side view of combine

FIG. 2 is an overall plan view of the combine

[Fig. 3] Vertical rear view of the drafting device

FIG. 4 is a schematic diagram showing a transmission structure.

FIG. 5 is a vertical cross-sectional side view of essential parts showing the configuration of the lifting device.

FIG. 6 is a vertical cross-sectional rear view of the main part showing the configuration of the lifting device.

FIG. 7 is a schematic diagram showing a transmission structure in a mission case.

FIG. 8 is a vertical cross-sectional rear view of the main part of the configuration of the second transmission.

FIG. 9 is a vertical cross-sectional rear view of essential parts showing a low speed forward state of the second transmission.

FIG. 10 is a vertical cross-sectional rear view of essential parts showing a high speed forward state of the second transmission.

FIG. 11 is a vertical cross-sectional rear view of a main part showing a reverse state of the second transmission.

FIG. 12 (a) A vertical sectional side view of a main portion showing a steering lever linkage structure. (B) A vertical sectional front view of a main portion showing a steering lever linkage structure.

FIG. 13 is a cross-sectional plan view of a main portion showing a linkage structure of a control lever.

FIG. 14 is a vertical cross-sectional rear view of essential parts showing a neutral state of a control lever.

FIG. 15 is a vertical cross-sectional rear view of a main portion showing a turning operation state of a control lever.

FIG. 16 is a rear view of a main part showing a linkage structure for a side clutch brake.

FIG. 17A is a vertical cross-sectional side view of an essential part showing a lowering operation state of the control lever. FIG. 17B is a vertical side view of an essential part showing a raising operation state of the control lever.

FIG. 18 is a side view of a main part showing a linkage structure for an operation pedal and an operation lever.

FIG. 19 is a rear view of the main part showing the structure for linking the operation pedal and the operation lever.

FIG. 20 is a plan view of an essential part showing a linkage structure for an operation pedal and an operation lever.

FIG. 21 is a schematic view showing another transmission structure in the mission case.

FIG. 22 is a vertical cross-sectional side view of a main part showing the linkage structure of the operation tool.

FIG. 23 is a vertical cross-sectional side view of essential parts showing a forward speed increasing operation state of the operation tool.

FIG. 24 is an enlarged side view of a main part showing the linkage structure of the operation tool.

FIG. 25 is a vertical cross-sectional rear view of the main part showing the linkage structure of the operation tool.

FIG. 26 is a cross-sectional plan view of a main part showing the linkage structure of the operation tool.

FIG. 27 is a plan view showing a movement operation path of an operation tool.

FIG. 28 is a partial vertical cross-sectional rear view of the main part showing the holding state of the holding mechanism.

FIG. 29 is a partial vertical cross-sectional rear view showing the neutral return start state by the neutral return mechanism.

FIG. 30 is a vertical cross-sectional front view of essential parts showing the configuration of the outer wheel.

FIG. 31 is a schematic view showing another embodiment of a shift operation structure.

[Explanation of symbols]

3 working devices 46 First Transmission 61 Second Transmission 65 Moving member 68 ball detent mechanism 76 balls 77 recess 78 Boss 125 controls 169 Work transmission

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Claims (10)

[Claims] 1. A work device drive for transmitting power to a work device by operating a first transmission that is a continuously variable transmission and operating a second transmission that shifts power after shifting by the first transmission. A power transmission structure for a working machine configured to switch between a state and a state in which the working apparatus is stopped without transmitting power to the working apparatus. 2. The gear shift operation structure for a work machine according to claim 1, wherein the second transmission is a stepped transmission. 3. The gear shift operation structure for a work machine according to claim 1, wherein the work device is configured to drive the work device in the normal direction regardless of whether the work device is driven forward or backward. 4. A shift moving member mounted on the second transmission shows the working device stopped state in association with the appearance of a reverse state by the operation of the first transmission or the second transmission. The gear shift operation structure for a working machine according to claim 1 or 2, wherein 5. A shift moving member provided in the second speed change device is configured to cause the working device stop state to appear in association with the appearance of a high speed transmission state due to operation of the second speed change device. The gearshift operation structure for a working machine according to claim 1. 6. The driving speed of the work device is changed to a speed according to the traveling speed after the shift by the second transmission device in association with the operation of the second transmission device in the working device driving state. The transmission structure for a working machine according to any one of claims 1 to 5, further comprising a work transmission. 7. A structure in which the transmission shaft mounted on the second transmission is slid to change the speed of the second transmission and to switch between the working device driven state and the working device stopped state. The transmission structure for a working machine according to any one of claims 1 to 6. 8. A transmission shaft mounted on the second transmission device slides to shift the second transmission device, switch between the working device driving state and the working device stopped state, and the working transmission device. 7. The configuration is such that the gear shifting is performed.
Transmission structure of the work machine described. 9. The transmission shaft is a rotating shaft, and the ball is spring-biased in a state of being installed in the transmission shaft and protruding from a peripheral surface thereof, and integrally rotatable and relatively slidable on the transmission shaft. The transmission shaft is held at a desired gear shift position from a cylindrical boss that is externally fitted to the transmission shaft and has a plurality of ring-shaped recesses formed on the fitting surface of the transmission shaft to allow engagement of the balls. 8. A ball detent mechanism is configured.
Alternatively, the power transmission structure of the working machine according to 8. 10. The work according to claim 1, wherein the operation of the first transmission and the second transmission is configured to be performed by a movement operation of a single operation tool. Machine transmission structure.