KR20100070317A - Work vehicle - Google Patents

Abstract

PURPOSE: A work car is provided to improve the turning performance of a work car by differentiating the velocity of left and right driving gears. CONSTITUTION: A work car comprises: a first swiveling gear which differentiates the velocity of left and right driving gears and swivels a body; a second swiveling gear which largely differentiates the velocity of left and right driving gears than the first swiveling gear and swivels a body; a swiveling setting unit(78) which sets a first state wherein the first swiveling gear drives or a second state wherein the second swiveling gear drives; a steering operation part(77) which is artificially operated; and a control unit(64). The first swiveling gear is composed of a grand turn mechanism which transfers power in low speed to the right or left driving gear. The second swiveling gear is composed of a brake mechanism which brakes the right or left driving gear.

Description

WORK VEHICLE}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a work vehicle having traveling devices on the right and left sides, and more particularly, to a steering operation structure of a work vehicle configured to impart a speed difference to the traveling devices on the right and left sides to perform steering operation of the aircraft. will be.

In a combine, which is an example of a work vehicle, as shown in JP2000-335268 A, a speed difference is given to the right and left traveling devices (reference numeral 1 in Figs. 1 and 2) and the right and left traveling devices so that the aircraft is connected. 2nd turning mechanism (reference numeral 49, 50 of FIG. 2) which turns a body by giving the speed difference larger than a 1st turning mechanism to the 1st turning mechanism (45 of FIG. 2) to make turning, and the right and left traveling apparatuses. There is a thing with).

In JP2000-335268 A, a swing setting means (reference numerals 71 and 55 in FIG. 3) capable of setting a first state in which the first swing mechanism operates or a second state in which the second swing mechanism operates, a steering control mechanism artificially operated (Reference numeral 58 in Fig. 4) is provided.

Thereby, when the steering operation tool is operated to the straight position, the power in the same direction is transmitted to the traveling devices on the right and the left at the same speed, and the gas moves straight.

In the first state, when the steering operating tool is operated to the right, for example, the first turning mechanism is in an operating state, and the aircraft turns to the right by the speed difference between the right and left traveling devices. The larger the operation to the right, the greater the speed difference between the right and left traveling devices, so that the aircraft turns to the right with a small turning radius. Also in the second state, when the steering operation tool is operated to the right, for example, the second turning mechanism is in the operating state, and the body turns to the right as described above.

When the 1st and 2nd turning mechanisms which give a speed difference to the right and left traveling devices like JP 2000-335268 A have a room for improvement in terms of the improvement of turning performance and operability of turning operation.

In the steering operation structure of a work vehicle, the present invention includes first and second swing mechanisms for providing a speed difference to right and left traveling devices, and a first state or second swing mechanism in which the first swing mechanism operates. The object of the present invention is to improve the swing performance of the work vehicle and the operability of the swing operation when the swing setting means capable of setting the second state in which the wheel is operated is provided.

In order to achieve the above object, a first feature configuration of a work vehicle according to the present invention is to configure a steering operation structure as follows.

The first turning mechanism which gives a speed difference to the right and left traveling apparatuses, the right and left traveling apparatuses, and turns a gas, and the right and left traveling apparatus gives a speed difference larger than a 1st turning mechanism, A second swing mechanism for swinging is provided.

Swing setting means which can set the 1st state in which a 1st turning mechanism operates, or the 2nd state in which a 2nd turning mechanism operates, and a steering operating tool artificially operated are provided.

The first turning mechanism is operated so that the speed difference between the right and left traveling devices becomes larger as the steering operating tool is operated from the straight position to the right or the left in the first state, and the steering operating tool is right from the straight position in the second state. Or control means for manipulating the second swing mechanism such that the speed difference between the right and left travel devices becomes larger as it is operated to the left.

In a 1st state, it is comprised so that the unit speed difference by the 1st turning mechanism with respect to the unit operation amount of a steering operation tool may be small in the area | region on the side of the straight position of a steering operation tool, and large in the area | region on the steering limit side of a steering operation tool.

In a 2nd state, it is comprised so that the unit speed difference by the 2nd turning mechanism with respect to the unit operation amount of a steering operation tool may be small in the area | region on the side of the straight position of a steering operation tool, and large in the area | region on the steering limit side of a steering operation tool.

The change characteristic of the unit speed difference of a 1st state and the change characteristic of the unit speed difference of a 2nd state are set to another thing.

According to the first feature configuration, in the first state (second state), when the steering operation tool is operated to the right (left) side, the first turning mechanism (second turning mechanism) is in an operating state and the right and left travels. Due to the speed difference of the device, the aircraft changes direction to the right (left) side, and the larger the steering control is operated to the right (left) side, the larger the speed difference of the right and left traveling devices, and the aircraft has the right (with a small turning radius). Change direction to the left).

In this case, in a state in which the steering operating tool is operated in the area on the straight position side (a state in which the steering operating tool is operated slightly to the right or left from the straight position), the speed difference between the right and left traveling devices becomes relatively small. As compared with the operation of the steering operation tool, the base is in a state in which the direction is changed to the right (left) side relatively smoothly, and thus, the base is suitable for the state of fine adjustment of the direction of the base when going straight. This is especially suitable for the first state.

Next, in the state where the steering operating tool is operated in the region on the steering limit side (state in which the steering operating tool is operated largely to the right or left from the straight position), the speed difference between the right and left traveling devices becomes relatively large, and the steering is performed. Compared to the operation of the operation tool, the body is in a state of changing direction to the right (left) side with a small turning radius, so that the body is suitable for a state of rapidly changing the direction of the body. This is especially suitable for the second state.

Further, according to the first feature configuration, the change characteristic of the unit speed difference in the first state and the change characteristic of the unit speed difference in the second state are set to be different.

Thereby, since the occurrence state (occurrence characteristic) of the speed difference of the right and left traveling devices when the steering operation tool is operated from the straight position to the steering limit is different from the first and second states, the first and the second The difference in the turning characteristic of the 1st and 2nd states becomes large compared with the structure in which the above-mentioned generation | occurrence | production state (generation characteristic) of the speed difference in 2 states is the same, and the 1st and 2nd appropriate | suitable according to the state of a work paper and a work type 2 states are easy to set.

Therefore, in the first and second states, the unit speed difference by the first and second turning mechanisms relative to the unit operation amount of the steering operation tool is small in the area on the side of the straight position of the steering operation tool, and in the area on the steering limit side of the steering operation tool. The larger the point and the larger the difference in the turning characteristics of the first and second states, the easier the first and second states can be set depending on the state of the work paper and the work type, and the turning performance and turning of the work vehicle. It was possible to improve the operability of the operation.

In the second aspect of the present invention, the change characteristic of the unit speed difference in the first and second states is such that the unit speed difference in the first state is smaller than the unit speed difference in the second state in the region on the straight position side of the steering operation tool. Is setting. This is further advantageous in the following points.

In the first state, in a state in which the steering operating tool is operated in the area on the straight position side (a state in which the steering operating tool is operated slightly to the right or left from the straight position), the speed difference between the right and left traveling devices is It becomes relatively small, and compared with the operation of the steering operation tool, the base is in a state in which the direction is gradually changed to the right (left) side, and therefore, the base is suitable for a state of fine-tuning the direction of the base when going straight.

In this case, according to the second feature, in the first state in which the gas is turned by giving a relatively small speed difference to the traveling devices on the right and left sides, the above-described state is obtained. Fine adjustment of the direction of the gas is consistent in terms of characteristics (characteristic that the direction of the gas does not change so much), so that the driver can fine-tune the direction of the gas at the time of going straight without discomfort.

Therefore, the turning performance of the work vehicle and the operability of the turning operation could be further improved.

In a third aspect of the invention, the first swing mechanism is a grand turn mechanism that transmits low-speed power to the other side of the right or left travel device in the same direction as one of the right or left travel devices. The second swing mechanism is a brake mechanism that brakes the traveling device on the right or left side.

In a 4th characteristic structure of this invention, a 1st turning mechanism is a complete turning mechanism which transmits a low speed power to the other side of a right or left travel device in the same direction as one of the right or left travel devices, and a 2nd turning mechanism Is a reverse rotation mechanism that transmits power in a reverse direction with one of the right or left travel devices to the other of the right or left travel devices.

If the third feature configuration or the fourth feature configuration is provided in addition to the second feature configuration, a sufficient difference is given to the swing characteristics of the first and second states by the complete swing mechanism, the brake mechanism or the reverse rotation mechanism, so that the state of the work paper It is easy to set the appropriate first and second states depending on the type of work.

Therefore, the difference of the turning characteristic of a 1st and 2nd state becomes large, and it is easy to set the appropriate 1st and 2nd state according to the state of a work paper and a work type, and the turning performance of a work vehicle and the operability of turning operation improve. Could be planned.

In addition to the said 2nd characteristic structure, the 5th characteristic structure of this invention has the following structures.

The first swing mechanism is a complete swing mechanism that transmits low-speed power to the other side of the right or left travel device in the same direction as one of the right or left travel devices, and the second swing mechanism is connected to the right or left travel device. It is a brake mechanism to apply braking. And a reverse rotation mechanism that transmits power in a reverse direction to one of the right or left travel devices to the other of the right or left travel devices.

By the swing setting means, a first state in which the complete swing mechanism is used, a second state in which the brake mechanism is used, and a third state in which the reverse rotation mechanism is used can be set. In the region on the straight position side of the steering operation tool, the change characteristic of the unit speed difference in the second and third states is set so that the unit speed difference in the second state is smaller than the unit speed difference in the third state.

According to the fifth feature configuration, by providing the complete swing mechanism, the brake mechanism and the reverse rotation mechanism, sufficient difference is given to the swing characteristics of the first, second and third states, so that the selection range is widened according to the state of the work paper or the work type. Appropriate first, second, and third states are easily set.

Further, in the region on the straight position side of the steering operation tool, the unit speed difference in the first state is set to be smaller than the unit speed difference in the second state, and the unit speed difference in the second state is smaller than the unit speed difference in the third state. The change characteristic of the unit speed difference of the 1st, 2nd, and 3rd states is set to the thing different from each other. Thereby, the difference of the turning characteristic of a 1st, 2nd, 3rd state becomes large, a selection range becomes wider according to the state of a work paper and a work form, and it becomes easy to set suitable 1st, 2nd, 3rd state.

Therefore, the 1st, 2nd, and 2nd and 3rd states widen the selection, and the difference in the turning characteristics of the 1st, 2nd, and 3rd states becomes large. The three states were easily set and improved the swing performance of the work vehicle and the operability of the swing operation.

In addition to the said 2nd characteristic structure, the 6th characteristic structure of this invention has the following structures.

The first swing mechanism is a complete swing mechanism that transmits low-speed power to the other side of the right or left travel device in the same direction as one of the right or left travel devices, and the second swing mechanism is connected to the right or left travel device. It is a brake mechanism to apply braking. And a reverse rotation mechanism that transmits power in a reverse direction to one of the right or left travel devices to the other of the right or left travel devices.

By the swing setting means, a first state in which the complete swing mechanism is used, a second state in which the brake mechanism is used, and a third state in which the reverse rotation mechanism is used can be set. In the region on the side of the straight position of the steering operation tool, the change characteristic of the unit speed difference in the second and third states is set so that the unit speed difference in the second state and the unit speed difference in the third state are the same.

According to the sixth feature configuration, by providing the complete swing mechanism, the brake mechanism and the reverse rotation mechanism, a sufficient difference is given to the swing characteristics of the first, second and third states, so that the selection range is widened according to the state of the work paper or the work type. Appropriate first, second, and third states are easily set.

Further, in the region on the straight position side of the steering operation tool, the unit speed difference in the first state is set to be smaller than the unit speed difference in the second state, and the unit speed difference in the second state and the unit speed difference in the third state are the same. It is set to be. Thereby, the difference in the turning characteristic of the 1st, 2nd, 3rd state does not become large unnecessarily large, and it becomes easy to set the appropriate 1st, 2nd, 3rd state according to the state of a work paper and a work form.

Therefore, it is appropriate to select the appropriate conditions according to the state of the work paper and the type of work by the point that the selection range is widened by the first, second and third states, and the difference in the turning characteristics of the first, second and third states is not unnecessarily large. The 1, 2, and 3 states were easily set, and the swing performance of the work vehicle and the operability of the swing operation could be improved.

Other features and advantages will become apparent from the following description with reference to the accompanying drawings.

In the following description, unless otherwise specified, the combine as an example of the work vehicle is referred to as a front-rear direction on the basis of the direction going forward (forward), and the horizontal direction orthogonal to this front-rear direction is referred to as the left-right direction (or lateral direction). The direction perpendicular | vertical to the front-back direction and the left-right direction is called an up-down direction.

In the steering operation structure of a work vehicle, the present invention includes first and second swing mechanisms for providing a speed difference to right and left traveling devices, and a first state or second swing mechanism in which the first swing mechanism operates. When the turning setting means which can set the second state in which is operated is provided, the turning performance of the work vehicle and the operability of the turning operation can be improved.

1 to 6 are views showing the first embodiment.
1 is an overall side view of a combine.
Figure 2 is a longitudinal front view of the mission case, the right and left transmission case;
Fig. 3 is a longitudinal front view of the vicinity of a grand turn clutch, a brake, a reverse clutch, and right and left side clutches of a mission case;
4 is a diagram showing a hydraulic circuit structure in the hydraulic unit.
Fig. 5 is a diagram showing a relationship between a shift lever, a steering lever, a swing mode switch, a hydrostatic stepless speed change gear, and a hydraulic unit.
Fig. 6 is a solid line (grand turn) showing the relationship between the operating position of the steering lever and the operating current of the proportional control valve (operating pressure of the complete turning clutch), the operating position of the steering lever and the operating current of the proportional control valve ( Solid line indicating the relationship between the operating pressure of the brake (pivot turn), and solid line indicating the relationship between the operating position of the steering lever and the operating current of the proportional control valve (operating pressure of the reverse clutch). turn)].
7 to 16 are diagrams showing a second embodiment;
7 is a side view of the work machine.
8 is a side view of the crawler traveling device.
9 is a plan view of a crawler traveling device.
10 is a side view of a crawler traveling device rear part;
11 is a longitudinal plan view of a crawler tensioning device.
12 is a longitudinal side view of the crawler tensioning device.
Fig. 13 is a plan view of the crawler guide mounting structure.
14 is a perspective view of the crawler guide mounting portion and the intermediate member.
15 is a plan view of a wheel support;
Figure 16 is a side view of the wheel support.
17 to 35 are diagrams showing a third embodiment,
17 is an overall side view of the combine.
18 is a side view of the grain tank.
19 is a top view of the grain tank.
20 is a perspective view of the grain tank viewed from the inside of the body;
21 is a schematic diagram of an electric system.
Fig. 22 is a longitudinal side view showing the linkage structure of the bottom screw and the longitudinal conveyance mechanism.
Fig. 23 is an exploded cross sectional view showing a linkage structure between a vertical conveyance mechanism and a horizontal conveyance mechanism;
24 is a rear view of the grain tank.
Fig. 25 is a plan view showing the swing drive structure of the grain dispensing device;
Fig. 26 is a rear view showing the carrying out portion of the grain tank.
Fig. 27 is a perspective view showing the rear part of the grain tank.
Fig. 28 is a perspective view showing a state where the movable cover at the bottom of the grain tank is open;
Fig. 29 is a transverse plan view showing the clutch on state of the electric system from the engine to the bottom screw;
30 is a cross sectional plan view showing the clutch off state of the electric system from the engine to the bottom screw;
Fig. 31 is a longitudinal side view showing the transmission structure of the bottom screw front end portion.
32 is a front view showing the drive structure of the falling guide plate;
33 is a front view seen from the axial direction of the clutch member.
34 is a cross-sectional view of the clutch member.
Fig. 35 is an exploded view showing a coupling recess in the clutch member.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described, referring drawings. Hereinafter, although some embodiment is described, the combination of the characteristic of one embodiment and the characteristic of another embodiment is also considered to be included in the scope of the present invention.

[First Embodiment]

[One]

As shown in Fig. 1, the harvesting frame 2 is supported by the crawler traveling device 1 (corresponding to the traveling device) on the right and left sides so that the harvesting frame 2 can be lifted around the transverse center P1. The lifting cylinder 3 which raises and lowers the harvesting frame 2 is provided, and the harvesting part 4 is supported by the harvesting frame 2. An operating part 5 is provided on the right side of the front part of the body, a threshing apparatus 8 is provided on the left side of the back part of the body, and a grain tank 9 is provided on the right side of the back part of the body, an example of a work vehicle. A phosphorus combine combines.

Next, the mission case 10 will be described.

As shown in Figs. 1 and 2, the mission case 10 is provided near the left and right centers of the front part of the base, and a stepped recess 10a is formed on the upper right side of the mission case 10. The hydrostatic stepless speed change apparatus 11 is connected so as to enter the recess 10a of the mission case 10. Right and left support portions 10b are provided outside the lower portion of the mission case 10 so that the right and left transmission cases 14 are connected to the right and left support portions 10b of the mission case 10 to the front side. It is extended.

1 and 2, the right and left axle cases 15 are connected to the right and left transmission cases 14 and extend to the right and left sides, and the right and left crawler traveling devices 1 The sprocket 1a for driving) is provided at the right and left ends of the right and left axle cases 15. The connection part 10c is provided in the outer part of the lower part of the mission case 10, and the linking member 13 is connected across the connection part 10c of the mission case 10, and the transmission case 14 of the right and left sides.

[2]

Next, the structure of the electric system (straight line system) in the mission case 10 is demonstrated.

As shown in Fig. 2, the power of an engine (not shown) is transmitted to an input shaft (not shown) of the hydrostatic stepless speed changer 11 through a transmission belt (not shown), and the hydrostatic stepless speed change is shown. The output shaft 11a of the apparatus 11 is inserted inside the mission case 10. The input shaft 22 is supported on the upper part of the mission case 10, and the electric gears 23 and 24 are fixed to the input shaft 22, and the output shaft 11a of the hydrostatic stepless speed changer 11 has a spline structure. It is connected to the transmission gear 24 (input shaft 22) by this.

As shown in FIG. 2, the high speed gear 25 and the low speed gear 26 are externally rotatably inserted into the transmission shaft 27 supported on the upper part of the mission case 10, and the transmission gear 23 and The high speed gear 25, the electric gear 24, and the low speed gear 26 mesh with each other, and the shift member 28 is externally inserted into the electric shaft 27 by a spline structure so as to be integrally rotatable and slidable. The sub transmission device is comprised by the transmission gear 23, the high speed gear 25, the electric gear 24, the low speed gear 26, and the shift member 28, and the shift member 28 is made into the high speed and low speed gear ( By engaging with 25 and 26, the power of the input shaft 22 is shifted to the high and low two stages (high speed and low speed positions), and is transmitted to the transmission shaft 27. Usually, the shift member 28 slides to the position which meshes with the high gear 25, and the high speed position is set.

2 and 3, the transmission shaft 29 is supported over the lower part of the mission case 10, the transmission gear 31 is fixed to the left side of the transmission shaft 29, and the transmission shaft The transmission gear 30 is being fixed to the left side of 27, and the transmission gears 30 and 31 are meshed. The right and left output gears 32R and 32L are externally inserted to the transmission shaft 29 so as to be relatively rotatable, and on the right and left sides of the right and left output gears 32R and 32L, the right and left engagement portions ( 33R and 33L are externally inserted in the rotating shaft 29 so that they may be integrally rotated and slidable by the spline structure. The right side clutch 34 is configured between the right output gear 32R and the right engaging portion 33R, and the left side clutch (34) between the left output gear 32L and the left engaging portion 33L. 34) is configured.

As shown in Fig. 2, the transmission shaft 35 is supported over the right and left support portions 10b and the right and left transmission cases 14 of the mission case 10, The transmission gear 36 fixed to the transmission shaft 35 inside is engaged with the output gears 32R, 32L on the right and left sides, and the transmission shaft 35 inside the transmission case 14 on the right and left sides. ), The electric gear 37 is fixed. The right and left axles 38 are supported over the right and left transmission cases 14 and the right and left axle cases 15, and the inside of the right and left transmission cases 14 is the right side. And the transmission gear 39 fixed to the left axle 38 meshes with the transmission gear 37. Inside the right and left axle cases 15, the right and left axles 38 extend right and left, and the sprocket 1a of the right and left crawler traveling apparatus 1 (see Fig. 1). Is connected to the right and left ends of the right and left axles 38.

With the above structure, as shown in Fig. 2, the power of the input shaft 22 is driven by the transmission shaft 27, the transmission gears 30 and 31, the transmission shaft 29, and the right and left side clutches 34 (right side). And left engaging portions 33R, 33L], right and left output gears 32R, 32L, transmission gear 36, transmission shaft 35, transmission gears 37, 39, right and left axles ( Via 38), the gas travels straight to the crawler traveling device 1 on the right and left sides.

[3]

Next, the right and left side clutches 34 will be described.

As shown in FIG. 3, the spline part 29a is formed in the outer surface of the right side and the left side of the transmission shaft 29, and the engagement part 33R, 33L of the right and left sides is the spline part of the transmission shaft 29 ( The housing member 40 is rotatably externally inserted into the spline portion 29a of the transmission shaft 29 so as to be integrally rotated and slidably externally inserted into the 29a).

As shown in Fig. 3, a plurality of concave portions are disposed along the circumferential direction at portions on the housing member 40 side in the right and left engaging portions 33R and 33L, and the right and left engaging portions 33R are shown. , The spring 41 is disposed on the inside and the outside of each of the recesses of the 33L, and the right and left engaging portions 33R and 33L are right and left by the housing member 40 and the spring 41. Is pushed toward the engaging side of the output gears 32R and 32L. The right and left engaging portions 33R and 33L are engaged with the right and left output gears 32R and 32L, so that the right and left side clutches 34 are in an electric state, and the power of the electric shaft 29 It is transmitted to the crawler traveling apparatus 1 of the right and left side by the side clutch 34 of the right and left side.

As shown in Fig. 3, the piston 42 is slidably arranged between the right and left output gears 32R and 32L and the transmission shaft 29, and the piston 42 is the right and left engaging portion ( Spring pins across the right and left engagement portions 33R, 33L and the piston 42 so that the piston 42 and the right and left engagement portions 33R, 33L rotate integrally. (43) is inserted.

As shown in Fig. 3, when hydraulic oil is supplied between the right and left output gears 32R and 32L and the piston 42, the right and left engagement portions 33R and 33L and the piston 42 are springs 41. ) And slides toward the spaced side of the right and left output gears 32R and 32L, and the left and right side clutches 34 are blocked. When hydraulic oil is discharged between the right and left output gears 32R and 32L and the piston 42, the right and left engagement portions 33R and 33L and the piston 42 are output by the spring 41 to the right and left sides. It slides to the engagement side of gear 32R, 32L, and it becomes the transmission state of the side clutch 34 of the right side and the left side.

[4]

Next, the structure of the electric system (turning system) in the mission case 10 is demonstrated.

As shown in FIGS. 2 and 3, the transmission shaft 44 is supported over the mission case 10, and the transmission gear 45 externally inserted to the right side of the transmission shaft 44 so as to be relatively rotatable is right. Is engaged with the gear portion of the outer circumference of the engaging portion 33R, and is a complete turning clutch 46 (corresponding to the first turning mechanism and a grand turn mechanism between the transmission shaft 44 and the transmission gear 45). Equivalent to) is provided. The complete swing clutch 46 is configured in a friction multi-plate type, and is operated in an electric state by supplying hydraulic oil, and operated in a shut off state by discharging hydraulic oil.

As shown in Figs. 2 and 3, the swing clutch case 47 is externally inserted in the transmission shaft 29 so as to be relatively rotatable, and the transmission gear 48 and the rotation clutch case fixed to the transmission shaft 44 are fixed. The electric gear 47a of the outer peripheral part of 47 is engaged. The swing clutch case 47 is formed symmetrically, and the right and left swing clutch 49 is provided between the swing clutch case 47 and the right and left output gears 32R and 32L. The right and left swing clutches 49 are configured in a friction multi-plate type, and are operated in an electric state by supplying hydraulic oil. In this case, in the right and left swing clutch 49, the friction plates are arranged to be in close contact with each other, and the right and left swing clutch 49 are configured to be in the reverse dynamic state even when the hydraulic oil is discharged.

As a result, when the complete swing clutch 46 is operated in the electric state as shown in Figs. 2 and 3, the power of the electric shaft 29 is engaged with the right engaging portion 32R, the electric gear 45, and the complete swing. The clutch 46, the transmission shaft 44, and the transmission gear 48 are transmitted to the swing clutch case 47 as power lower than that of the transmission shaft 29 by rotation in the same direction as the transmission shaft 29. When the right or left side clutch 34 is operated in a blocked state, and the right or left swing clutch 49 is operated in an electric state, rotation of the right or left side clutch 34 in the same direction as that of the electric shaft 29 results in a lower speed than that of the electric shaft 29. Power is transmitted to the output gears 32R and 32L on the right or left side.

2 and 3, the brake 50 (corresponding to the second turning mechanism) (corresponding to the brake mechanism) is provided on the left side of the transmission shaft 44. As shown in FIG. The brake 50 is composed of a friction multi-plate type and operated in a braking state by supplying hydraulic oil, and operated in a released state by discharging the hydraulic oil.

As a result, when the brake 50 is operated in a braking state as shown in Figs. 2 and 3, the turning clutch case 47 is brought into a braking state through the transmission shaft 44 and the transmission gear 48. If the right side or left side clutch 34 is operated in a shut-off state, and the right side or left side turning clutch 49 is operated in an electric state, the right or left output gears 32R, 32L are put into a braking state.

2 and 3, the transmission gear 51 is fixed to the left side of the transmission shaft 27, and the transmission gear 52 is externally inserted to the left side of the transmission shaft 44 so as to be relatively rotatable. , The electric gears 51 and 52 are engaged with each other, and the reverse rotation clutch 53 (corresponding to the second swing mechanism) (corresponding to the reverse rotation mechanism) is provided between the transmission shaft 44 and the transmission gear 52. . The reverse rotation clutch 53 is composed of a friction multi-plate type, and is operated in an electric state by supplying hydraulic oil, and operated in a blocked state by discharging the hydraulic oil.

As a result, as shown in Figs. 2 and 3, when the reverse clutch 53 is operated in the electric state, the power of the electric shaft 27 is driven by the electric gears 51 and 52, the reverse clutch 53, and the electric shaft. Through 44 and the transmission gear 48, it is transmitted to the turning clutch case 47 as rotational power reverse to the transmission shaft 29. As shown in FIG. When the right side or left side clutch 34 is operated in the blocked state, and the right side or left side turning clutch 49 is operated in the electric state, rotational power in the opposite direction to the transmission shaft 29 is output to the right or left side output gear 32R. , 32L).

[5]

Next, operation of the hydrostatic stepless speed change apparatus 11 will be described.

As shown in Fig. 5, the pump 11P of the hydrostatic continuously variable transmission 11 is endlessly moved from the neutral position N, the neutral position N to the high speed side of the forward F and the high speed side of the reverse R. It is comprised so that a shift is possible, and the motor 11M of the hydrostatic stepless speed change apparatus 11 is comprised so that shifting is possible in two steps of height. The hydraulic cylinder 59 for operating the inclined plate of the pump 11P of the hydrostatic stepless speed change apparatus 11 and the control valve 60 for supplying and operating hydraulic oil to the hydraulic cylinder 59 are provided. The shift lever 61 and the control valve 60 provided are mechanically linked. Thereby, the control valve 60 is operated by operating the shift lever 61, the hydraulic cylinder 59 is operated, and the pump of the hydrostatic stepless speed change apparatus 11 at a position corresponding to the operation position of the shift lever 61. The inclined plate of 11P is operated.

As shown in Fig. 5, the hydraulic cylinder 62 for operating the inclined plate of the motor 11M of the hydrostatic continuously variable transmission 11, and the electromagnetically operated control valve for supplying and operating hydraulic oil to the hydraulic cylinder 62 ( 63 is provided, the shifting switch 61a is provided in the holding part of the shifting lever 61, and the operation signal of the shifting switch 61a of the shifting lever 61 corresponds to the control device 64 (control means). ) Is entered. Thereby, by operating the shifting switch 61a of the shift lever 61, the control valve 63 is operated by the control apparatus 64, the hydraulic cylinder 62 is operated, and the motor of the hydrostatic stepless speed change apparatus 11 is operated. The inclined plate of 11M is operated in the high speed and low speed positions.

Angles of the swing mode switch 78, grand turn, pivot turn and spinner turn as described in [7], [8], [9], and [10] described later. In the state, it is possible to select the complete turning state, the new ground swing state and the super-ground swing state by the swing mode switch 78 as the hydrostatic stepless speed change device 11 by the shift switch 61a of the shift lever 61. It is a state in which the inclination plate of 11M of motors of () is operated by the low speed position. If the inclined plate of the motor 11M of the hydrostatic stepless speed changer 11 is operated at the high speed position by the shifting switch 61a of the shift lever 61, the complete line is completed regardless of the operating position of the swing mode switch 78. The time state is selected.

[6]

Next, the right and left side clutch 34 (right and left engagement portions 33R, 33L), the right and left swing clutch 49, the complete clutch 46, the brake 50, and the reverse rotation The hydraulic unit 57 which supplies and distributes hydraulic oil to the clutch 53 is demonstrated.

As shown in Fig. 4, a charge pump (not shown) and a hydraulic pump 56 are connected to an input shaft (not shown) of the hydrostatic CVT 11, The charge pump and the hydraulic pump 56 are driven by the input shaft, and the hydraulic oil of the charge pump is supplied to the hydrostatic stepless speed change apparatus 11. As shown in Figs. 2 and 3, the hydraulic unit 57 is connected to the outer surface of the left and right sides of the mission case 10, and the external pipe 58 (see Fig. 4) from the hydraulic pump 56 is hydraulic. It is connected to the unit 57.

2 and 3, the left ends of the transmission shafts 29 and 44 penetrate the left and right side portions of the mission case 10 and are inserted into the hydraulic unit 57, and the left ends of the transmission shaft 29 are shown. A flow path 29b is provided inside the transmission shaft 29 over the side clutch 34 (right and left engagement portions 33R, 33L) of the right side and the left side and the swing clutch 49 of the right side and the left side. It is. The flow path 44a is provided inside the transmission shaft 44 over the left end of the transmission shaft 44, the complete swing clutch 46, and the reverse rotation clutch 53. As shown in FIG. The brake 50 is provided in the edge part of the transmission shaft 44 inside the hydraulic unit 57.

As shown in FIG. 4, the priority control valve 67, the left turn control valve 68, the relief valve 69, the unload valve 70, and the proportional control valve 71 are provided inside the hydraulic unit 57. And the swing switching control valve 72 and the pilot operation valves 73 and 74 are provided. The external piping 58 from the hydraulic pump 56 is connected to the hydraulic unit 57, and many flow paths (shown in the connection surface (alignment surface) of the hydraulic unit 57 and the left-right side part of the mission case 10 are shown in figure). And the right and left swing control valves 67 and 68, the relief valve 69, and the unload valve 70 are connected to the flow path 66 connected to the external pipe 58 (fitting surface). Are connected in parallel via a flow path. The drain flow path is formed in the connection surface (fitting surface) of the hydraulic unit 57 and the left-lateral side part of the mission case 10, and the hydraulic oil of the relief valve 69 and the unload valve 70 is transmitted through the above-mentioned drain flow path. Return to the mission case 10.

As shown in Fig. 2, the priority control valve 67 has the right side clutch 34 (the right engaging portion 33R on the right side) through the flow path of the connection surface (alignment surface) and the flow path 29b of the transmission shaft 29. ) And the swing clutch 49 on the right side. The left pivot control valve 68 is connected to the left side clutch 34 (left engaging portion 33L) and the left pivot via the flow path on the connection surface (alignment surface) and the flow path 29b of the transmission shaft 29. (49).

As shown in Fig. 4, the right and left swing control valves 67 and 68 are electromagnetically operated that can be operated at the supply positions 67a and 68a and the discharge positions 67b and 68b, and the discharge positions 67b and 68b. ) Is being pressed. The unload valve 70 is constituted by an electromagnetic operation type which can be operated at the cutoff position 70a and the discharge position 70b, and is pushed to the cutoff position 70a. The proportional control valve 71 and the swing switching control valve 72 are connected in series to the flow path 75 branched from between the right and left swing control valves 67 and 68 and the flow path 29b of the transmission shaft 29. The swing switching control valve 72 is connected to the full swing clutch 46 and the reverse rotation clutch 53 via the flow path of the connection surface (alignment surface) and the flow path 44a of the transmission shaft 44. The switching control valve 72 is connected to the brake 50 via the oil passage 76 of the hydraulic unit 57.

As shown in Fig. 4, the proportional control valve 71 is electromagnetically operated so that the flow rate control (pressure control) of the working oil is possible. The swing switching control valve 72 is comprised by the pilot operation type which can be operated in the complete swing position 72a, the new swing position 72b, and the ultra-new swing position 72c, and is pressed to the complete swing position 72a. The pilot operation valve 73 is configured to supply the pilot hydraulic oil branched from the oil passage 75 to the swing switching control valve 72 to operate at the Shinji swing position 72b, and pivot the pilot hydraulic oil branched from the oil passage 75. The pilot operation valve 74 is comprised so that it may supply to the switching control valve 72, and to operate to the super paper turning position 72c.

The right and left swing control valves 67 and 68, the unload valve 70, the proportional control valve 71 and the pilot operation valves 73 and 74 are described later in [7], [8], [9] and [10]. As described in the reference].

[7]

Next, the straight state by the steering lever 77 will be described.

As shown in Fig. 5, a steering lever 77 (corresponding to a steering operation tool) that can be artificially operated on the right side and the left side is provided in the driving unit 5, and the operation position of the steering lever 77 is controlled by the control unit 64. ), The steering lever 77 is configured to be operated in the straight position (N), the first turning position (R1, L1) of the right and left, the second turning position (R2, L2) of the right and left It is. The swing mode switch 78 (corresponding to the swing setting means) is provided in the driving unit 5, the operation position of the swing mode switch 78 is input to the control device 64, and the swing mode switch 78 is The complete swing position (corresponding to the first state), the shinji swing position (corresponding to the second state), and the supernew swing position (corresponding to the second and third states) are provided.

4 and 5, regardless of the operating position of the swing mode switch 78, when the steering lever 77 is operated to the straight position N, the right and left swing control valves 67 and 68 are discharged. Operating in positions 67b, 68b, unloading valve 70 operated in discharge position 70b, right and left side clutches 34 (right and left engagement portions 33R, 33L), right and The hydraulic oil is discharged from the left swing clutch 49, the right and left side clutches 34 (right and left engaging portions 33R, 33L) are operated in an electric state, and the right and left swing clutch 49 are operated. ) Is operated in a reverse motion. By means of the proportional control valve 71, the complete swing and reverse rotation clutches 46 and 53 are operated in the blocked state, and the brake 50 is operated in the released state.

As a result, the power of the input shaft 22 causes the power of the transmission shaft 27, the transmission gears 30 and 31, the transmission shaft 29, and the right and left sides as described in Figs. 2 and 2 to [4] and [4]. Clutch 34 (right and left engagement portions 33R, 33L), right and left output gears 32R, 32L, transmission gear 36, transmission shaft 35, transmission gears 37, 39, The gas travels straight through the right and left axles 38 to the right and left crawler traveling devices 1.

[8]

Next, the complete turning state by the steering lever 77 will be described.

As shown in Figs. 4 and 5, when the swing mode switch 78 is operated to the full swing position, the swing switching control valve 72 is operated to the full swing position 72a by the pilot operation valves 73 and 74. . Thereby, when the steering lever 77 is operated to the 1st turning position R1 of the right side, the priority control valve 67 will operate to the supply position 67a, and the unload valve 70 will move to the cutoff position 70a. The operating oil is supplied to the right side clutch 34 (right engaging portion 33R) and the right turning clutch 49 to shut off the right side clutch 34 (right engaging portion 33R). The steering wheel 49 on the right side is operated in an electric state.

In this case, as shown in Figs. 2 and 3, since the left turning clutch 49 is in the reverse motion state, the power of the left side clutch 34 (the left engaging portion 33L) is controlled by the left output gear 32L. ) And left swing clutch 49 (semi-electrical state) are transferred to right output gear 32R via right swing clutch 49 (electrical state) and rotated in the same direction as transmission shaft 29. Power slightly lower than the transmission shaft 29 is transmitted to the output gear 32R on the right side. As a result, the body gently turns to the right.

As shown in Figs. 4 and 5, when the steering lever 77 is operated to the first turning position R1 on the right side, the priority control valve 67 is operated to the supply position 67a and unloaded as described above. The valve 70 is operated to the shutoff position 70a and at the same time, hydraulic oil is supplied to the complete clutch 46 through the proportional control valve 71 and the swing switching control valve 72 (full swing position 72a). By operating the steering lever 77 from the first turning position R1 on the right side to the second turning position R2 on the right side, the operating pressure of the complete turning clutch 46 is boosted by the proportional control valve 71. (As shown in Fig. 6, the solid line A1 (the complete turning state) showing the relationship between the operating position of the steering lever 77 and the operating current of the proportional control valve 71 (the operating pressure of the complete clutch 46). ) Reference}.

As shown in Figs. 2 and 3, the operating shaft 29 of the complete clutch 46 is stepped up and down by the proportional control valve 71 based on the operating position of the steering lever 77. Power of the right engaging portion 33R, the electric gear 45, the complete swing clutch 46, the electric shaft 44, the electric gear 48, the swing clutch case 47 and the right swing clutch 49 The lower-speed power than the transmission shaft 29 is transmitted to the output gear 32R on the right side by the rotation in the same direction as the transmission shaft 29 via.

In this case, as shown in Figs. 2 and 3, the power from the left side clutch 34 (the left engaging portion 33L) and the power from the complete swing clutch 46 simultaneously operate the right output gear ( 32R), the operating pressure of the complete swing clutch 46 is in the low pressure range (the state in which the steering lever 77 is operated near the right first swing position R1). 34) The power from [the left engaging part 33L] beats the power from the full swing clutch 46, and outputs the right side by the power from the left side clutch 34 (the left engaging part 33L). The gear 32R is driven so that the gas gently turns to the right.

Next, when the steering lever 77 is operated from the first turning position R1 on the right side to the second turning position R2 on the right side, and the operating pressure of the complete turning clutch 46 is slightly elevated, FIGS. As shown in the figure, the power from the complete swing clutch 46 overcomes the power from the left side clutch 34 (the left engaging portion 33L) and is driven by the power from the complete swing clutch 46 to the right. 32R is driven. In this state, the right side is driven by the power from the complete turning clutch 46 than the right side output gear 32R is driven by the power from the left side clutch 34 (the left engaging portion 33L). Of the output gear 32R of the right side causes the output gear 32R of the right side to be driven at a low speed, and the body makes a full turn to the right side, and the steering lever 77 moves to the second turning position R2 side of the right side. As it is operated, the turning radius of the gas decreases.

As shown in Figs. 4 and 5, when the steering lever 77 is operated to the left first swing position L1, the left swing control valve 68 is operated to the supply position 68a, and the unload valve 70 ) Is operated to the cutoff position 70a, and hydraulic oil is supplied to the left side clutch 34 (the left engaging portion 33L) and the left swing clutch 49 to supply the left side clutch 34 (the left side). Engaging portion 33L] is operated in the blocking state, and the leftward clutch 49 is operated in the electric state. At the same time, the same operation as described above is performed, and the base gently turns to the left. When the steering lever 77 is operated from the first swing position L1 on the left side to the second swing position L2 side on the left side, the same operation as described above is performed, and the base is turned to the left side.

[9]

Next, the Shinji turning state by the steering lever 77 is demonstrated.

As shown in Figs. 4 and 5, when the swing mode switch 78 is operated in the new swing position, the swing switching control valve 72 is operated by the pilot operating valves 73 and 74 in the new swing position 72b. . Thereby, when the steering lever 77 is operated to the 1st turning position R1 of the right side, the priority control valve 67 will operate to the supply position 67a, and the unload valve 70 will move to the cutoff position 70a. The operating oil is supplied to the right side clutch 34 (right engaging portion 33R) and the right turning clutch 49 to block the right side clutch 34 (right engaging portion 33R). The steering wheel 49 on the right side is operated in an electric state. In this case, since the swing clutch 49 on the left side is in a reverse motion state, the body gently turns to the right side as in the preceding paragraph [8].

As shown in Figs. 4 and 5, when the steering lever 77 is operated to the first pivot position R1 on the right side, the priority control valve 67 is operated to the supply position 67a and the unload valve as described above. The operating oil 70 is supplied to the brake 50 through the proportional control valve 71 and the swing switching control valve 72 (new swing position 72b) while the 70 is operated to the cutoff position 70a. As the steering lever 77 is operated from the first turning position R1 on the right side to the second turning position R2 on the right side, the operating pressure of the brake 50 is boosted by the proportional control valve 71 (Fig. As shown in FIG. 6, see the solid line A2 (new swing state) which shows the relationship between the operation position of the steering lever 77, and the operation current of the proportional control valve 71 (operating pressure of the brake 50).

As shown in Figs. 2 and 3, the operating pressure of the brake 50 is boosted by the proportional control valve 71 based on the operating position of the steering lever 77. (48), the braking force is applied to the right output gear 32R via the turning clutch case 47 and the right turning clutch 49, and the braking force becomes stronger.

In this case, as shown in Figs. 2 and 3, the power from the left side clutch 34 (the left engaging portion 33L) and the braking force of the brake 50 are simultaneously the right output gear 32R. The operating pressure of the brake 50 is in a low pressure range (a state in which the steering lever 77 is operated in the vicinity of the first turning position R1 on the right side). Of the engaging portion 33L] overcomes the braking force of the brake 50, and the right output gear 32R is driven by the power of the left side clutch 34 (left engaging portion 33L). . As a result, when the operating pressure of the brake 50 is low, the gas gently turns to the right.

Next, when the steering lever 77 is operated from the first turning position R1 on the right side to the second turning position R2 on the right side and the operating pressure of the brake 50 is slightly elevated, as shown in FIGS. 2 and 3. As described above, the braking force of the brake 50 overcomes the power from the left side clutch 34 (the left engaging portion 33L) so that the right output gear 32R is braked by the braking force of the brake 50. As a result, the body turns to the right side, and the turning radius of the body decreases as the steering lever 77 is operated to the second turning position R2 side on the right side.

As shown in Figs. 4 and 5, when the steering lever 77 is operated to the first turning position L1 on the left side, the left turning control valve 68 is operated to the supply position 68a, and the unload valve 70 Is operated to the cutoff position 70a, hydraulic oil is supplied to the left side clutch 34 (the left engaging portion 33L) and the left turning clutch 49, and the left side clutch 34 (the left engaging) is operated. 33L) is operated in a cutoff state, and the swing clutch 49 on the left side is operated in an electric state. At the same time, the same operation as described above is performed, and the base gently turns to the left. When the steering lever 77 is operated from the first swing position L1 on the left side to the second swing position L2 side on the left side, the same operation as described above is performed, and the base is swung to the left.

As shown in Figs. 4 and 5, a steering switch 77a is provided at the gripping portion of the steering lever 77. As described in the foregoing paragraph [8], the swing mode switch 78 is operated to the full swing position, and the steering lever 77 moves from the first swing position R1 (L1) on the right (left) side to the right (left). In the right or left full swing state operated at the second swing position R1 (L1) on the side, it is assumed that there is a need for turning to a smaller radius.

In this case, as shown in Figs. 4 and 5, the steering lever 77 is moved from the first turning position R1 (L1) on the right (left) side to the second turning position R1 (on the right (left) side). L1)], when the steering switch 77a of the steering lever 77 is pressed and operated, the swing switching control valve 72 is operated from the complete swing position 72a to the Shinji swing position 72b, and the gas is turned right. We turn to Shinji (left) side. This new swing state is only while the steering switch 77a of the steering lever 77 is being pushed and operated, and when the hand is released from the steering switch 77a of the steering lever 77, the swing switching control valve 72 is operated. Is operated from the Shinji swing position 72b to the complete swing position 72a and the body returns to the complete swing state.

[10]

Next, the super paper turning state by the steering lever 77 will be described.

As shown in Figs. 4 and 5, when the swing mode switch 78 is operated in the supersize swing position, the swing switching control valve 72 is moved to the supersize swing position 72c by the pilot operation valves 73 and 74. Manipulated. Thereby, when the steering lever 77 is operated to the right 1st turning position R1, the priority control valve 67 will operate to the supply position 67a, and the unload valve 70 will operate to the cutoff position 70a. Then, hydraulic oil is supplied to the right side clutch 34 (right engaging portion 33R) and the right pivoting clutch 49 so that the right side clutch 34 (right engaging portion 33R) is blocked. The swing clutch 49 on the right side is operated in an electric state. In this case, since the swing clutch 49 on the left side is in the reverse dynamic state, the body gently turns to the right side as in the preceding paragraph [8].

As shown in Figs. 4 and 5, when the steering lever 77 is operated to the first pivot position R1 on the right side, the priority control valve 67 is operated to the supply position 67a and the unload valve as described above. The operating oil 70 is supplied to the reverse rotation clutch 53 through the proportional control valve 71 and the swing switching control valve 72 (the paper conveying swing position 72c) while the 70 is operated to the cutoff position 70a. As the steering lever 77 is operated from the first turning position R1 on the right side to the second turning position R2 on the right side, the operating pressure of the reverse rotation clutch 53 is boosted by the proportional control valve 71. 6 (solid line turning indicating the relationship between the operating position of the steering lever 77 and the operating current of the proportional control valve 71 (operating pressure of the reverse rotation clutch 53) (refer to FIG. 6). Status)}.

As shown in Figs. 2 and 3, the operating pressure of the reverse rotation clutch 53 is stepped up by the proportional control valve 71 based on the operating position of the steering lever 77. The power is driven through the transmission gears 51 and 52, the reverse clutch 53, the transmission shaft 44, the transmission gear 48, the swing clutch case 47 and the swing clutch 49 on the right side. It is transmitted to the output gear 32R on the right side as rotation power in the reverse direction.

In this case, as shown in Figs. 2 and 3, the power from the left side clutch 34 (the left engaging portion 33L) and the power from the reverse rotation clutch 53 simultaneously operate the right output gear ( 32R), the operating pressure of the reverse rotation clutch 53 is in the low pressure range (the steering lever 77 is operated at the first turning position on the right side (in the vicinity of R1)). 34) Power from the left engaging portion 33L overcomes the power from the reverse rotation clutch 53, and outputs the right side by the power from the left side clutch 34 (the left engaging portion 33L). The gear 32R is driven. As a result, when the operating pressure of the reverse rotation clutch 53 is low, the gas gently turns to the right.

Next, when the steering lever 77 is operated from the first turning position R1 on the right side to the second turning position R2 on the right side and the operating pressure of the reverse rotation clutch 53 is slightly boosted, Figs. As shown in the figure, the power from the reverse clutch 53 overcomes the power from the left side clutch 34 (the left engaging portion 33L) and is output from the right by the power from the reverse clutch 53. 32R is driven. In this state, the output gear 32R on the right side is driven in the reverse direction with respect to the output gear 32L on the left side, and the body pivots on the right side to the right side, and the steering lever 77 is on the second turning position R2 on the right side. As it operates to the side, the turning radius of a gas becomes small.

As shown in Figs. 4 and 5, when the steering lever 77 is operated to the left first swing position L1, the left swing control valve 68 is operated to the supply position 68a, and the unload valve 70 ) Is operated to the cutoff position 70a, and hydraulic oil is supplied to the left side clutch 34 (the left engaging portion 33L) and the left swing clutch 49 to supply the left side clutch 34 (the left side). Engaging portion 33L] is operated in the blocking state, and the swing clutch 49 on the left side is operated in the electric state. At the same time, the same operation as described above is performed, and the base gently turns to the left. When the steering lever 77 is operated from the first swing position L1 on the left side to the second swing position L2 side on the left side, the same operation as described above is performed, and the base body pivots to the left.

[11]

The operating position of the steering lever 77 and the operating current of the proportional control valve 71 in the complete swing state, new swing state and super-since swing state described in the above-mentioned [8], [9], [10]. The relationship of the operating pressure of the rotary clutch 46 becomes a relationship shown by the solid line A1 (full swing state) of FIG. 6, and the operating position of the steering lever 77 and the operating current of the proportional control valve 71 (brake ( 50) is a relationship represented by the solid line A2 (new swing state) in FIG. 6, and the operating position of the steering lever 77 and the operating current of the proportional control valve 71 (reverse clutch 53). Operating pressure] is represented by a solid line A3 (transmission paper turning state) in FIG.

The solid lines A1 (full swing state), A2 (new swing position), and A3 (super-signage swing state) are quadratic curves shown in the following formulas B1, B2, and B3.

B1 (A1 (full swing state)): Y1 = a11, X, X-a21, X + a31

B2 (A2 (new ground turning state)): Y2 = a12, X, X-a22, X + a32

B3 (A3 (super shin turning state)): Y3 = a13, X, X-a23, X + a33

only

X: Operation position of steering lever 77

Y1: operating current of the proportional control valve 71 (operating pressure of the full swing clutch 46)

Y2: operation current of the proportional control valve 71 (operating pressure of the brake 50)

Y3: operating current of the proportional control valve 71 (operating pressure of the reverse clutch 53)

a11 to a33: positive integer

Thereby, in the complete swing state, the new ground swing state, and the super-ground swing state, the unit operation current of the proportional control valve 71 with respect to the unit operation amount of the steering lever 77 (the swing clutch 46, the brake 50). And unit speed difference generated in the crawler traveling device 1 on the right and left sides by the reverse rotation clutch 53 (unit speed difference in the first and second states) are set on the right and left sides of the steering lever 77. It is small in the area | region of 1 turning position R1, L1 side (straight position N side), and large in the area | region of the right and left 1st turning position R2, L2 side (steering limit side) of steering lever 77. It is.

In this case, in positive integers a11 to a33,

a11> a12> a13

a21> a22> a23

a31> a32> a33

Relationship is established, and as shown in Fig. 6, the equations B1 [A1 (full swing state)], equations B2 [A2 (new swing state)], and equations B3 [A3 (supernatant swing state)] are different from each other. It is a quadratic curve. As a result, the turning characteristics are different in the complete turning state, the new ground turning state, and the super-thin turning state (in a state where the change characteristic of the unit speed difference in the first state and the change characteristic of the unit speed difference in the second state are different). Equivalent).

As shown in Fig. 6, by the relationship between the positive integers a11 to a33 described above, in the region of the first turning position R1, L1 side (straight position N side) on the right and left sides of the steering lever 77 The unit of the proportional control valve 71 with respect to the unit operation amount of the steering lever 77 in the new swing position is greater than the unit operation current of the proportional control valve 71 with respect to the unit operation amount of the steering lever 77 in the super-new swing state. The operating current is small. The unit operation current of the proportional control valve 71 with respect to the unit operation amount of the steering lever 77 in the full swing state is greater than the unit operation current of the proportional control valve 71 with respect to the unit operation amount of the steering lever 77 in the new swing state. It is small.

[First Other Embodiment of First Embodiment]

In the complete swing state, the Shinji swing state and the super Shinji swing state of the above-described [First Embodiment], if any one of the states (1) (2) (3) described below is established, the shift lever 61 You may be comprised so that operation of the motor 11M of the hydrostatic stepless speed change apparatus 11 by the shifting switch 61a to high speed position (refer to previous item [5]) cannot be performed.

(1) The steering lever 77 is operated between the first right and second right swing positions R1 and R2 (between the first left and second left swing positions L1 and L2). condition.

(2) The steering lever 77 is operated between the first right and second right swing positions R1 and R2 on the right side (between the first left and second swing positions L1 and L2 on the left side), In addition, the traveling speed of the aircraft is a high speed more than the set speed.

(3) Steering lever 77 is an intermediate position between first right and second right swing positions R1 and R2 (intermediate position between first left and second swing positions L1 and L2 on the left). ] Is operated to the right 2nd turning position R2 side (left 2nd turning position L2 side).

[2nd another form of 1st Embodiment]

In the complete swing state, the Shinji swing state and the super Shinji swing state of the above-mentioned [First Embodiment], if any one of the states (1) (2) (3) described below is established, the shift lever 61 You may be comprised so that operation of the motor 11M of the hydrostatic stepless speed change apparatus 11 by the shifting switch 61a to high speed position (refer to previous item [5]) cannot be performed.

(1) The speed difference is generated in the crawler traveling apparatus 1 of the right and left sides by operating the complete turning clutch 46, the brake 50, and the reverse rotation clutch 53. FIG.

(2) By operating the complete turning clutch 46, the brake 50, and the reverse rotation clutch 53, a speed difference occurs in the crawler traveling device 1 on the right and left sides, and the traveling speed of the body is higher than the set speed. State.

(3) The speed difference occurs in the crawler traveling apparatus 1 of the right and left sides by operating the complete turning clutch 46, the brake 50, and the reverse rotation clutch 53, and the speed difference is more than the set speed difference.

[Third Other Form of First Embodiment]

In the above-mentioned [first embodiment], [first other embodiment of the first embodiment], and [second other embodiment of the first embodiment], the reverse rotation clutch 53 is abolished, and the complete clutch 46 ) And the brake 50 may be provided. In this configuration, the complete swing clutch 46 becomes the first swing mechanism, and the brake 50 becomes the second swing mechanism.

In the above-described [first embodiment], [first other embodiment of the first embodiment], and [second other embodiment of the first embodiment], the brake 50 is abolished, and the complete clutch 46 You may comprise so that the reverse rotation clutch 53 may be provided. If comprised in this way, the complete turning clutch 46 will be a 1st turning mechanism, and the reverse rotation clutch 53 will be a 2nd turning mechanism.

[4th another form of 1st Embodiment]

In the above-mentioned [first embodiment], [first other embodiment of the first embodiment] to [third other embodiment of the first embodiment], the characteristics of the Shinji swing state {Formula B2 [A2 (new Shin swing state)) ]} And the characteristics of the new paper swing state (formula B3 [A3 (new paper swing state)]) may be the same (in this case, a12 = a13, a22 = a23, and a32 = a33).

[Fifth Other Embodiment of First Embodiment]

In above-mentioned [1st Embodiment], [1st Other Embodiment of 1st Embodiment]-[4th Other Embodiment of 1st Embodiment], Formula B1 [Al (full swing state)], Formula B2 [A2 (Shinji turning state)] and the formula B3 [A3 (supersignal turning state)] are not constituted by a quadratic curve, but by combining a plurality of straight lines (first order function) with different inclination characteristics as shown in FIG. You may comprise so that this may be obtained.

Second Embodiment

Next, a second embodiment will be described with reference to FIGS. 7 to 16.

In this second embodiment, in the crawler tension adjusting device of the crawler traveling device provided with the ground front wheels 124, 125, and 126 rotatably positioned to one horizontal side of the track frame 122,

A guide member 152 and a guide member 152 positioned on a horizontal side where the grounding rollers 124, 125, and 126 of the track frame 122 are positioned and supported by the track frame 122, and the guide member 152. Tension supported on the crawler belt 129 by being supported by the tension adjusting frame 151 so as to be slidably moved in the front and rear direction of the track frame, and the wheel support 150 of the tension adjusting frame 151. A tension wheel 127 and a tension adjustment mechanism 155 for slidingly adjusting the tension adjustment frame 151 with respect to the guide member 152,

The wheel support portion 150 is characterized by having a two-pronged shape for supporting the tension wheel 127 on both transverse sides.

As the above-mentioned crawler tensioning device, there is one described in JP2005-335614 A (see paragraph [0019], Fig. 3).

The crawler tension adjusting device described in this document includes a bracket inserted slidably back and forth at the rear end of the track frame, and a tension wheel axially rotatably supported by the bracket.

The tension wheel adjusts the tension of the crawler belt by screwing the bracket by rotating the operating shaft.

The crawler tension adjusting device includes a support shaft extending from the bracket to one side horizontally, and by supporting the tension wheel on the extension end side of the support shaft, the front wheels for grounding the track frame are positioned so that the tension wheel is properly wound and rotated. It is located on one side horizontally.

In this crawler tension adjusting device, when a strong tension is generated in the crawler belt, such as during turning, if a large deformation occurs in the supporting member such as the support shaft of the tension wheel, displacement of the tension wheel may occur, and the crawler belt may be easily peeled off. . For this reason, it is necessary to firmly support the tension wheel so that even if a strong tension is generated in the crawler belt, the displacement of the tension wheel does not occur. In the above conventional crawler tension adjusting device, the support shaft of the tension wheel is supported by only one side of the tension wheel. When the support of the tension wheel is firmly performed, the support shaft becomes thicker and the weight is increased.

On the other hand, according to the structure of this embodiment, the wheel support part of the tension adjustment frame 151 is employ | adopted by employ | adopting the guide member 152 located on the horizontal side where the ground front wheels 124, 125, and 126 of the track frame 122 are located. The grounding front wheels 124 and 125 of the track frame 122 have a two-pronged shape that supports the tension wheel 127 on both sides while the 150 is rotated so that the crawler belt 143 is properly wound. , 126 may be positioned on one side of the horizontal. Thereby, the support shaft of the tension wheel 127 is supported on both lateral sides of the tension wheel 127, and the support shaft of the tension wheel 127, the tension adjustment frame 151, etc. are employ | adopted compact compared with the conventional thing, Even when a strong tension is generated in the crawler belt 129, the tension wheel 127 may be firmly supported so that there is no displacement of the operation.

Therefore, the crawler tension adjusting device can be obtained in which the weight of the tension wheel support structure is reduced while the support of the tension wheel 127 is firmly performed so that the crawler belt 129 cannot be easily peeled off.

Suitably, the guide member 152 is configured to slide and guide the tension adjustment frame 151 with the tension wheel 127 ascending relative to the track frame 122 as the tension wheel 127 moves away from the guide member 152. Doing. This is advantageous in the following points.

As for the load by the crawler belt 129 of the tension wheel 127, the tension generated in a portion located above the tension wheel 127 of the crawler belt 129 in the direction along the track frame 122 And a tension with the tension generated at a portion located below the tension wheel 127 in an inclined direction with respect to the track frame 122 are applied to the tension wheel as the tension of the crawler belt 129.

According to this configuration, the direction of the load applied to the tension wheel 127 by the tension of the crawler belt 129 is the direction along the direction in which the tension adjusting frame 151 is guided and moved to the guide member 152, or In the near direction, the tension adjusting frame 151 can be slid and adjusted while making it difficult to generate a twist between the guide member 152 and the tension adjusting frame 151.

Therefore, the twist between the guide member 152 and the tension adjustment frame 151 is less likely to occur, thereby obtaining a crawler tension adjustment device capable of smoothly and lightly adjusting the tension.

In addition, the tension adjusting mechanism 155 is disposed on the side opposite to the side where the track frame 122 is located with respect to the tension adjusting frame, and is provided over the guide member 152 and the tension adjusting frame 151. If it is, it is advantageous at the following points.

According to this structure, the tension adjustment mechanism 155 can be operated without the obstacle by the track frame 122 from the side opposite to the side where the track frame 122 is located with respect to the tension adjustment frame 151. FIG.

Therefore, a crawler tension adjusting device having good operability can be obtained so that the tension adjusting mechanism 155 can be operated without the obstacles of the track frame 122 to perform the tension adjustment comfortably and efficiently.

In addition, a guide mounting portion 144 supporting the crawler guide 143 which prevents the crawler belt 129 from peeling off the crawler belt 129 is installed on the track frame 122, and the tension adjusting frame ( It is also advantageous in the following point to provide the support part 144a which acts on the 151 support.

Since the guide mounting part 144 supports the crawler guide 143, it is equipped with the outstanding strength. Thereby, according to this structure, the tension adjusting frame 15l can be firmly supported using the guide installation part 144 as a support means.

Therefore, the crawler tension adjusting device capable of firmly supporting the tension adjusting frame 151 to smoothly adjust the tension of the crawler belt 129 can be obtained by a simple structure using the guide mounting portion 144 as the supporting means. .

Hereinafter, 2nd Embodiment is described in detail.

Fig. 7 is a side view of the work machine provided with the crawler tension adjusting device A according to the present embodiment. As shown in this figure, this work machine is constituted so as to be frequented by a pair of right and left crawler traveling devices 101 and 101, and a traveling gas provided with a driving part equipped with a driving seat 102, and the traveling gas. A threshing device 104 and a grain tank 105 having a harvesting unit 110 connected to a front portion of the gas frame 103 and arranged in a gas transverse direction on the rear side of the gas frame 103. Equipped.

This machine harvests rice and barley.

That is, the harvesting unit 110 includes a harvesting frame 111 connected to the front of the base frame 103 so as to be swingable up and down, and the harvesting frame 111 is swinged up and down by the lifting cylinder 112. As a result, a grass-diving tool 113 positioned in the transverse direction at the front end of the harvesting unit 110 descends near the ground, and the grass-diving tool 113 is elevated from the ground. Ascend Ascend and descend to non-working state.

When the traveling body is driven with the harvesting unit 110 in a descending working state, the harvesting unit 110 is arranged in the upright grain stems of the harvesting targets by each of the dividing holes 113 in the plurality of mounting apparatuses 114. The upright grain stem which is introduced and placed in the erecting device 114 corresponding to the grass dividing sphere 113, and erected by each erecting device 114 is mowed by one cutter type mowing device 115, The harvesting grain stem from the harvesting | reaping apparatus 115 is supplied to the start end of the threshing feed chain 104a of the threshing apparatus 104 by the supply apparatus 116. FIG.

The threshing apparatus 104 clamps and conveys the underlined side of the harvested grain stem to the gas rear side by the threshing feed chain 104a, and supplies the tip end side of the harvested grain stem to a feeding chamber (not shown), and threshes. The grain tank 105 collects and stores the threshing grain conveyed from the threshing apparatus 104.

8 is a side view of the crawler traveling device 101 on the left side. 9 is a plan view of the crawler traveling device 101 on the left side. The crawler traveling apparatus 101 on the right side has the same structure as the crawler traveling apparatus 101 on the left side, and illustration of the crawler traveling apparatus 101 on the right side is abbreviate | omitted. As shown in these figures, the crawler traveling device 101 includes a track frame 122 connected to the base frame 103 through a pair of support arms 120 and 121 and the track frame 122. ) And a drive rotatable crawler drive wheel 123 supported on the base frame 103 through a mission case (not shown) above the front side; The eight loosely rotatable ground front wheels 124, 125, 126 arranged side by side in the track frame front and rear direction and supported by the track frame 122, and the rearmost track frame of the eight ground front wheels 124, 125, 126. The tension wheel 127 located at the rear end of the ground front wheel 126 located at the end side and installed at the rear end of the track frame 122, and above the track frame 122 to the body frame 103. A pair of loose back before and after And a rotatable carrier roller 128, 128, wherein the crawler drive wheel 123, the eight ground front wheels 124, 125, 126, the tension wheel 127, and the front and rear pair of carrier rollers 128, A rubber crawler belt 129 wound around the belt 128 is provided.

The support arm 120 on the front side includes a rotation support shaft 120a in which a base of the support arm 120 is rotatably connected to the base frame 103, and the support of the rotation support shaft 120a. It is interlocked with the cylinder rod 131a of the hydraulic cylinder 131 via the interlocking arm 130 installed so that the arm 120 is rotatably integrated in the opposite end to the side to which the arm 120 is connected.

That is, the support arm 120 on the front side is rocked up and down relative to the base frame 103 by the hydraulic cylinder 131 around the axis of the rotation support shaft 120a, and the front end side of the track frame 122. Is lifted and operated with respect to the base frame 103.

The support arm 121 on the rear side has a rotary support shaft 121a rotatably connected to the base frame 103 of the support arm 121 and the support arm of the rotary support shaft 121a. It is interlocked with the cylinder rod 133a of the hydraulic cylinder 133 via the interlocking arm 132 which is rotatably installed in the edge part on the opposite side to the side to which the 121 is connected. The loose end side of the support arm 121 on the rear side is connected to the rear end side of the track frame 122 via the cancel link 134.

That is, the support arm 121 on the rear side is rocked up and down relative to the base frame 103 by the hydraulic cylinder 133 around the axis of the rotary support shaft 121a, and through the cancel link 134. The rear end side of the track frame 122 is lifted and operated with respect to the base frame 103.

That is, the front and rear pairs of support arms 120 and 121 in the crawler traveling apparatuses 101 and 101 on the left and right sides are oscillated and the traveling body is inclined in the transverse direction and the front and rear direction with respect to the ground.

That is, the front and rear pairs of support arms 120, 121 in one side of the crawler traveling device 101 on the left and right are raised or lowered, and the front and rear pairs of support arms 120, 121 are raised or lowered. By rocking operation so that the stroke becomes the same, the track frame 122 on one side of the crawler traveling apparatus 101 on the left and right rises or descends in parallel with the base frame 103, and one end in the transverse direction of the traveling body The grounding point by the crawler traveling device 101 on the other end side is raised and lowered with respect to the ground as the swing support point.

In the crawler traveling apparatus 101 on the left and right sides, one of the front support arm 120 and the rear support arm 121 in the crawler traveling apparatus 101 on the left and right sides moves up or down. By rocking the support arms 120 and 121 so that the up or down strokes are the same, the track frame 122 of the crawler traveling device 101 on the left and right sides is moved to the base frame 103 with the ground point on the front end as the swing support point. Rock up and down, or swing up and down with respect to the gas frame 103 with the ground point on the rear end side as a rocking support point, and one end in the forward and backward direction of the traveling body ascending and lifting relative to the ground. .

Next, the ground front wheel 126 located at the rear end side of the track frame among the eight ground front wheels 124, 125, 126 is referred to as the last ground front wheel 126, and the eight ground front wheels 124, 125, The ground front wheel 125 located adjacent to the last ground front wheel 126 in front of the last ground front wheel 126 among the 126 will be described as the rear ground front wheel 125.

The rear ground front wheel 125 and the last ground front wheel 126 are supported by the track frame 122 so as to be loosely rotatable, and cannot be moved up and down with respect to the track frame 122.

Among the eight ground front wheels 124, 125, and 126, the ground front wheels 124 except for the last ground front wheel 126 and the rear ground front wheel 125 have two adjacent ground front wheels 124, 124. Grouped so as to form a front wheel group of the track frame 122, in which two ground front wheels 124 and 124 of each front wheel group are integrated and connected to the track frame 122 by one balance connecting member 140. Is supported).

As shown in Figs. 9 and 10, each balance connecting member 140 is rotatably supported by the track frame 122 via a connecting shaft 141 located at an intermediate portion thereof. One of the ground front wheels 124 of the two ground front wheels 124 and 124 forming each of the front wheel groups is loosely rotated at a portion located on the front side of the connecting shaft 141 of the balance connecting member 140. The other front ground wheel 124 is loosely supported at a portion located on the rear end side of the balance connecting member 140 from the connecting shaft 141.

As a result, the ground front wheels 124 excluding the last ground front wheels 126 and the rear ground front wheels 125 among the eight ground front wheels 124, 125, and 126, and two grounds forming the respective front wheel groups. The front wheels 124 and 124 are provided on the track frame 122 by the balance connecting member 140, and the track frame is made by swinging the balance connecting member 140 with the shaft center of the connecting shaft 141 as the swing support point. It moves up and down relative to 122.

The crawler traveling device 101 includes a crawler guide 142 installed in correspondence with the front wheel group, and a crawler guide 143 installed in correspondence with the rear ground front wheel 125 and the last ground front wheel 126. Doing.

As shown in Figs. 8 and 10, the crawler guide 142 corresponding to each of the front wheel groups is disposed between the left and right pairs of guide wheel bodies of one ground front wheel 124 of the front wheel group and the other side. A rod-shaped guide main body 142a positioned between a pair of left and right guide wheel bodies of the ground front wheel 124 and a connecting lever 142b connecting the guide main body 142a to the balance connecting member 140. It is comprised by the guide main body 142a, and it engages to the right and left core protrusions 129a and 129a of the crawler belt 129, and peels off the crawler belt 129. The crawler guide 142 corresponding to each front wheel group is manufactured by integrally casting the guide main body 142a and the connecting lever 142b together with the balance connecting member 140.

As shown in Fig. 10, the crawler guide 143 corresponding to the last ground front wheel 126 and the rear ground front wheel 125 is disposed between a pair of left and right guide wheel bodies of the rear ground front wheel 125; The guide body 143a of the rod shape located between the left and right guide wheel body parts of the last ground front wheel 126, and the guide installation part 144 which the track frame 122 equips this guide body 143a with Is connected to the core bar protrusions 129a on the left and right sides of the crawler belt 129 by the guide body 143a. Peeling is prevented. This crawler guide 143 is manufactured by integrally casting the guide main body 143a and the connecting lever 143b.

The guide mounting portion 144 of the track frame 122 is constructed by placing a metal block on the horizontal side of the track frame 122. The guide mounting portion 144 is arranged at the end of the guide mounting portion 144 by mounting three connecting bolts 145 arranged in a triangular arrangement in the vertical direction and the front and rear direction of the track frame 122, the crawler guide 143 To support the connection lever 143b.

The crawler traveling apparatus 101 is equipped with the crawler tension adjusting apparatus A which concerns on this embodiment provided in the rear part of the track frame 122. As shown in FIG.

Fig. 9 shows the structure in plan view of the crawler tension adjusting device A according to the present embodiment. Fig. 10 shows the structure when viewed from the side of the crawler tension adjusting device A according to the present embodiment. 11 is a vertical plan view of the crawler tension adjusting device A according to the present embodiment.

12 is a longitudinal side view of the crawler tension adjusting device A according to the present embodiment. As shown in these figures, the crawler tension adjusting device A according to the present embodiment includes the tension wheel 127 and the tension adjusting frame for loosely supporting the tension wheel 127 in the wheel support 150. 151, the guide member 152 supporting the tension adjusting frame 151, the engaging portion 153a protruding from the lateral side of the wheel support 150, and the guide member 152. The tension control shaft 155 provided over the support part 154 is comprised.

The tension adjustment frame 151 is provided with the frame main body 151a made of a square steel pipe member whose one end side is connected to the base of the wheel support part 150 in addition to the wheel support part 150.

15 is a plan view of the wheel support 150. 16 is a side view of the wheel support 150. As shown in these figures, the wheel support portion 150 has a two-pronged shaft having a pair of axial support holes 156a and 156a separated in both transverse sides of the tension wheel 127 and positioned. The support fork 156 is provided and comprised. As shown in Fig. 11, the wheel support 150 supports the support shaft 127a of the tension wheel 127 on both transverse sides of the tension wheel 127 by the shaft support fork 156. That is, the tension wheel 127 is supported on both lateral sides.

The guide member 152 is disposed on the same horizontal side as the horizontal side on which the ground front wheels 124, 125, and 126 of the track frame 122 are positioned, and a pair of front and rear support arms of the track frame 122 is provided. And the tension adjusting frame 151 is disposed at an appropriate position on one side of the track frame 122, that is, a position where the crawler belt 129 is appropriately wound around the tension wheel 127 and turned. Doing.

As shown in Figs. 12 to 14, an end portion of the side of the guide member 152 on which the tension adjustment frame 151 protrudes and the tension adjustment frame 151 are the installation portions of the track frame 122. It is supported by the said support part 144a from below from the support part 144a which consists of the upper end surface of 144 through the intermediate member 157 which carried the lower end part. The intermediate member 157 includes an upper sheet metal member 157a having one side acting on the lower surface of the guide member 152 and the tension adjusting frame 151, and between the upper sheet metal member 157a and the support 144a. It is comprised by the lower sheet metal member 157b interposed in.

The tension adjusting frame 151 is supported by the guide member 152 so that the frame main body 151a is slidably inserted into the guide member 152 so as to be slidable. Sliding is guided by the inner surface of the member 152 and slid in the front-rear direction of the track frame 122. The tension adjustment frame 151 is set to slide in accordance with the installation direction of the guide member 152, so that the tension wheel 127 slides with respect to the track frame 122 as it moves away from the guide member 152. do. In other words, the tension adjustment frame 151 is located above the tension wheel 127 of the crawler belt 129 and is positioned below the tension wheel 127 in the tension of the portion that is in the direction along the track frame 122. Thus, it is slid along the direction close to the direction of the load applied to the tension wheel 127 by the tension of the portion in the direction inclined with respect to the track frame 122.

The tension adjusting shaft 155 is constituted by a screw shaft screwed to the female screw of the adjusting shaft insertion hole provided in the support part 154 of the guide member 152, and when rotated, with respect to the guide member 152. The tension adjusting frame 151 is slid and adjusted with respect to the guide member 152 by moving in the front and rear direction of the track frame to push or pull the latching portion 153a of the wheel support 150. The tension adjusting shaft 155 is disposed on the side opposite to the side where the track frame 122 is located with respect to the tension adjusting frame 151, and the track frame 122 is located from the outside of the traveling body horizontally of the crawler traveling device 101. It can be operated without the obstacles caused by the operation.

As a result, the crawler tension adjusting device A slides the tension adjusting frame 151 to the guide member 152 and the intermediate member 157 by the tension adjusting shaft 155 by rotating the tension adjusting shaft 155. Adjust the movement while guiding. At this time, the tension adjustment frame 151 is slid along the direction close to the direction of the load applied to the tension wheel 127 by the tension of the crawler belt 129, the tension adjustment frame 151 and the guide member 152. It slides in a state where twisting is unlikely to occur. Then, the tension wheel 127 is moved and adjusted to the rear side with respect to the track frame 122 to adjust the tension force of the crawler belt 129 to the increasing side by pushing the crawler belt 129 toward the rear side of the traveling device more. Alternatively, the tension wheel 127 is moved to the front side with respect to the track frame 122 to reduce the pressure of the crawler belt 129 to adjust the tension force of the crawler belt 129 to the reduction side.

As shown in Figs. 15 and 16, the wheel support part 150 includes the shaft support fork 156 and the locking portion 153a, and is provided on the outer circumferential side of the shaft support fork 156. A pair of reinforcing ribs 158 and 158 and a second locking portion 153b provided on the side opposite to the side where the locking portion 153a is positioned with respect to the shaft support fork 156 are provided. The shaft supporting fork 156, the locking portion 153a, the reinforcing rib 158, and the second locking portion 153b are integrally cast by lost wax casting.

The second locking portion 153b is provided with a tension adjusting shaft 155 when the tension adjusting frame 151 is equipped with the crawler tension adjusting device A of the crawler traveling device 101 on the right side.

[Other Embodiments of Second Embodiment]

Instead of the embodiment described above, the object of the present invention can be attained even if a structure in which the tension adjusting frame 151 is slidably adjusted by a grease cylinder is employed. Therefore, the tension adjusting shaft 155, the grease cylinder, and the like are collectively referred to as a tension adjusting mechanism 155.

[Third Embodiment]

Next, a third embodiment will be described with reference to FIGS. 17 to 35.

In this 3rd Embodiment, the threshing apparatus 207 and the grain tank 208 are arrange | positioned side by side, and the engine 204 is arrange | positioned at the front side of the grain tank 208 laterally, and engine power is set to the said grain. In the grain recovery part drive structure of the combiner configured to be delivered to the front end of the bottom screw 210 of the tank 208,

While protruding the output shaft 263 from the engine 204 toward the outside of the body, the intermediate transmission shaft 271 is supported and bridged in the transverse direction to the front side of the grain tank 208, and the intermediate transmission shaft ( It is characterized in that the gas inner part of the 271 and the output shaft 263 is interlocked and at the same time the outer portion of the intermediate transmission shaft 271 and the front end of the bottom screw 210.

As a grain recovery part drive structure of a threshing apparatus, the output shaft which protruded in the gas direction from the engine arrange | positioned in the horizontal direction, and the gas inner side part of the intermediate transmission shaft arrange | positioned transversely to the front side of a grain tank are wound through an electric belt. It is known that it is configured to transmit the engine power to the front end of the bottom screw through the intermediate transmission shaft and the input case by interlocking the interlocking portion of the intermediate transmission shaft and the input case provided at the front of the grain tank. (See, eg, JP 9-205867 A).

In the above-described conventional structure, since the output shaft protruding from the engine is located far away from the bottom screw of the grain tank to the inside of the body, when the engine is installed inside the body for the left and right weight balance of the gas, the intermediate transmission shaft receiving the engine power is left and right. As long.

In particular, the grain tank is pivoted outside the body around the longitudinal support of the rear portion, and the transverse side portion of the threshing apparatus is largely opened, and the gas outer end of the intermediate transmission shaft and the input portion of the grain tank are configured to be disconnectable. In the case where the input of the grain tank is automatically separated from the intermediate transmission shaft in conjunction with the swing opening of the grain tank, and the input of the grain tank is automatically connected to the intermediate transmission shaft in conjunction with the return rotation of the grain tank. It is necessary to support the middle part of the intermediate transmission shaft with high accuracy by other shaft supporting members so that the long intermediate transmission shaft left on the base at the time of opening does not change position, which increases the number of parts constituting the transmission structure and increases the cost. There was a tendency.

On the other hand, according to the structure of this embodiment, even if the engine 204 is arrange | positioned inside a body, since the output shaft 263 protrudes toward the body horizontally outward from the engine 204, it spreads across the front side of the grain tank 208 horizontally. The interlocking position of the gas inner part of the intermediate transmission shaft 271 and the gas outer part of the intermediate transmission shaft 271 and the front end of the bottom screw 210 can be approached in the gas transverse direction, and the intermediate transmission shaft 271 ) Becomes short. The short intermediate transmission shaft 271 does not need to be supported in the middle.

Therefore, the transmission structure from the engine 204 to the bottom screw 210 of the grain tank 208 is made to be compact and simple in the transverse direction, while the engine 204 is installed inside the body to make the right and left weight balance of the gas suitable. Can be.

Suitably, the grain tank 208 is configured to be pivotable around a rearward longitudinal support point P, while an input case 251 is connected to the front portion of the grain tank 208, and the input case An input shaft 254 facing the inside of the body provided in 251 and the intermediate transmission shaft 271 are disposed to face each other in a concentric manner, and a clutch 273 for engaging and separating from the axial direction at the opposite portion is provided. This configuration is advantageous in the following points.

According to the above configuration, by turning the grain tank 208 out of the body, the interlocking of the intermediate transmission shaft 271 and the bottom screw 210 can be automatically interrupted, and greatly separated from the threshing apparatus 207, and the threshing apparatus ( Maintenance on the side of 207 can be easily performed from an open space. Since the input shaft 254 which receives the power from the intermediate transmission shaft 271 protrudes from the input case 251 in the direction of the body, the intermediate transmission shaft 271 can be made shorter by that amount.

Hereinafter, the third embodiment will be described in more detail.

Figure 17 shows a side view from the right side of the body of a whole culm discharging type combine-harvester. In this combine, the cutting part 203 of the multi-line cutting specification is movable up and down at the front part of the base frame 202 which has a pair of left and right crawler traveling apparatuses 201, The right side of the said base frame 202 is possible. The driving unit 205 and the driving unit 206 in which the engine 204 is built in the front part are disposed, and the threshing apparatus 207 is mounted on the left side of the gas frame 202, and the threshing apparatus 207 The grain tank 208 of sheet metal structure was equipped in the position which becomes the back side of the driving part 205 in the right side, The grain stem harvested by the harvesting | reaping part 203 is supplied to the threshing apparatus 207, and threshing process is carried out. The grains collected and collected by the threshing apparatus 207 are configured to be lifted by the screw-type grain grain apparatus 209 and put into the grain tank 208.

As shown in Figs. 20 and 24, the grain tank 208 is formed in a shape in which the lower portion thereof becomes narrower as viewed in the front-rear direction, and the graining device 209 is disposed on the left side facing the inside of the body. The vertically long recessed part 208a is formed. Before and after the longitudinally elongated recess 208a, recesses 208b and 208c are formed to avoid interference with the device portion projecting to the right side of the threshing apparatus 207, and the front of the longitudinally elongated recess 208a is formed. An enlarged bulge portion 208d is formed in the upper portion. Thus, large tank capacity is ensured by making the left side surface of the grain tank 208 approach the shape of the right side part of the threshing apparatus 207 as much as possible.

At the lower end of the narrowing portion 208e in the grain tank 208, the bottom screw 210 for sending the stored grains backward is supported and cross-linked horizontally back and forth through the support shaft 210a and at the same time the bottom screw 210 The flow guide plate 211 in which the cross-sectional shape was formed in the shape of a mountain along the upper side of the cross section) is supported and crosslinked so as to be able to swing through the rotating support shaft 212.

The narrowing portion 208e in the grain tank 208 is given an inclination angle equal to or more than the repose angle of the grain so as to guide the bottom screw 210 without leaving the stored grain, and the bottom screw 210 is provided with a gas frame. The lower end part of the part 208a narrowed so that it may be located outside 202 may be arrange | positioned to the horizontal outer side larger than the center of the tank width. In this way, the lower end of the narrowing portion 208e which accommodates the bottom screw 210 is positioned outside the gas frame 202 so that the lower end of the narrowing portion 208e of the grain tank 208 has the As compared with the case where it is located upward, the lower end of the narrowing part 208e of the grain tank 208 can be provided low, and by this, it is possible to increase the capacity by increasing the tank height (up and down length) without increasing the position of the tank upper end. It is possible.

The rear of the grain tank 208 is equipped with the screw type grain-feeding apparatus 213 which lifts the grains sent out by the bottom screw 210, and then transversely conveys them out of a gas. This grain dispensing apparatus 213 carries out the screw type longitudinal conveyance mechanism 213A connected in communication with the lower end part of the rear surface of the grain tank 208, and the screw type horizontal conveyance connected in communication with the upper end of this longitudinal conveyance mechanism 213A. It is comprised by the mechanism 213B, and the whole grain conveying apparatus 213 is pivotable about the screw axis of the longitudinal conveyance mechanism 213A and the concentric longitudinal support point p.

As shown in Fig. 22, the carrying case 214 for supporting the rear end of the support shaft 210a in the bottom screw 210 is connected to the lower rear end of the grain tank 208, and the gas frame 202 is connected. The lower end boss portion 214a of the carry-out case 214 is rotatably fitted to the support portion 202a protruding outward from the body horizontally, and the grain tank 208 moves around the longitudinal support point P. It is supported to be able to turn. As shown in FIG. 28, the lower front surface of the grain tank 208 is provided with the support plate 215 which consists of a thick plate material, and the lower end part of this support plate 215 is supported by the upper surface of the base frame 202, The total weight of the grain tank 208 is supported by the base frame 202 and the support part 202a in two places before and behind.

The support plate 215 is provided with a lock pin 220 to slide up and down. The lock pin 220 is pushed downward by the spring 221, and the grain tank 208 is predetermined by inserting the lower end of the lock pin 220 into the lock hole 222 formed in the gas frame 202 side. The grain tank 208 is pivoted around the longitudinal support point P by pulling the lock pin 220 out of the lock hole 222 against the spring 221. The right side of 207 can be moved to the maintenance position which opened large. In addition, the lock pin 220 is pulled up and rotated so that the lock pin 220 can be held by the housing member 223 provided in the support plate 215.

As shown in FIGS. 17-19 and 27, the side cover 225 which covers the tank side surface is fixedly connected to the horizontal outer side of the grain tank 208. As shown to FIG. The lower side cover 226 which covers the narrowing part 208e of the outward direction in the grain tank 208 from horizontally outer side is connected to the lower end part of the side cover 225. At the rear end of the side cover 225, the rear side side cover which covers most of the vertical conveyance mechanism 213A in the grain dispensing apparatus 213 from the horizontal side, and is provided with the work light 228, the vehicle width lamp 229, and the like. 227 is connected. The rear frame of the vertical conveying mechanism 213A is provided with a vertical frame 231 made of a square pipe standing up from the base frame 202, and covers the vertical conveying mechanism 213A from the rear from the rear. 230 is connected and fixed. When the grain tank 208 is pivoted outwardly around the longitudinal support point P, the rear side cover 227 pivoting integrally with the grain tank 208 is fixed as indicated by the imaginary line in FIG. It is supposed to return to the rear without interfering with the rear cover 230. As shown in Fig. 28, the front cover of the lower side cover 226 is equipped with a movable cover 232 so as to be able to swing open and close around the support point a in the longitudinal direction, and by opening the movable cover 232, The lock pin 220 is exposed so that the lock operation and the lock release operation of the grain tank 208 can be performed.

The vertical conveyance mechanism 213A in the said grain conveying apparatus 213 is comprised in which the longitudinal conveyance screw 236 was built in the longitudinal conveyance case 235 which consists of round pipe materials. As shown in FIG. 22, the lower end of the conveyance case 235 is rotatably inserted and supported around the longitudinal support point P with respect to the said carrying case 214, and at the two upper and lower positions of the said vertical frame 231. It is rotatably supported by the provided cylindrical support member 237, and the standing posture of the vertical conveyance mechanism 213A is maintained. The lower end of the support shaft 236a in the longitudinal feed screw 236 is inserted into the carry-out case 214, and the bevel gear is interlocked with the rear end of the support shaft 210a in the bottom screw 210. The longitudinal feed screw 236 is driven at the same speed as the bottom screw 210.

As shown in FIGS. 22 and 26, the grains sent out by the bottom screw 210 are guided to the conveyance region of the longitudinal conveying screw 236 in the longitudinal conveying mechanism 213A at the lower portion of the carrying case 214. The communication path R is formed, and the lower shape of the carrying case 214 and the grain tank 208 so that this communication path R may become a vertically long shape extended upward from the upper end of the bottom screw 210. The carrying out openings 208f are each formed in a vertical oval shape.

As shown in FIG. 23, the horizontal conveyance mechanism 213B of the said grain conveying apparatus 213 is carried out to the conveyance case 238 which consists of a round pipe material of the same diameter as the conveyance case 235 of the longitudinal conveyance mechanism 213A. A transverse feed screw 239 having a larger diameter support shaft 239a than the support shaft 236a of the longitudinal feed screw 236 is inserted therein, and the tip of the transfer case 238 is opened downward. The discharge port 240 is provided. The upper end part of the conveyance case 235 in the vertical conveyance mechanism 213A, and the base end of the conveyance case 238 in the horizontal conveyance machine 213B are connected and connected by the connection case 241. The connection case 241 is the upper end connection case part 241a fixed to the upper end part of the conveyance case 235 in the vertical conveyance mechanism 213A, and the base end part of the conveyance case 238 in the horizontal conveyance mechanism 213B. Consisting of a base end connecting case portion 241b fixed to the base end, and a base end connecting case portion 241b rotatably fitted to the upper end connecting case portion 241a so as to be rotatable around the lateral support point Q, thereby providing a horizontal conveyance mechanism. 213B is capable of swinging up and down around the lateral support point Q.

On the lateral support point Q, a relay shaft 242 is supported on both ends of the upper end connection case part 241a and the base end connection case part 241b. The relay shaft 242 is equipped with a feed vane 243 which is inclined with respect to the lateral support point Q, and at both ends of the relay shaft 242, the support shaft 236a in the longitudinal feed screw 236, respectively. The bevel gears are interlocked at the constant velocity at the upper end of the lateral end and the base end of the support shaft 239a in the horizontal feed screw 239. Thereby, the longitudinal feed screw 236 and the horizontal feed screw 239 are co-driven in synchronization with the rotation of the bottom screw 210, and the grains sent out from the grain tank 208 are lifted by the vertical conveying mechanism 213A. After that, it is horizontally conveyed by the horizontal conveyance mechanism 213B, and is discharged | emitted from the discharge port 240. FIG.

The relay shaft insertion through point in the connection case 241 is formed with a larger diameter than the conveyance case 238 of the conveyance case 235 of the longitudinal conveyance mechanism 213A and the transverse conveyance mechanism 213B, and the relay shaft 242 The cross-sectional area of the grain passage minus the cross-sectional area of the cross section) is set to be larger than the cross-sectional area of the grain passage minus the cross-sectional area of the grain passage minus the cross-sectional area of the support shaft in the longitudinal conveyance mechanism 213A and the cross section of the support shaft in the transverse conveyance mechanism 213B. Thus, the degree of freedom in grain movement in the connection case 241 is large, and grain transfer from the vertical transfer mechanism 213A to the horizontal transfer mechanism 213B is smoothly performed without clogging. The hydraulic cylinder 245 is constructed over the upper end connection case part 241a fixed to the said vertical conveyance mechanism 213A, and the conveyance case 238 of the horizontal conveyance mechanism 213B, and the expansion-contraction operation of this hydraulic cylinder 245 is carried out. As a result, the horizontal conveyance mechanism 213B is driven to swing up and down within a predetermined range around the horizontal axis Q. As shown in FIG.

As shown in Fig. 25, the carrying case 214 connected to and fixed to the bottom of the grain tank 208 is provided with an electric motor 246 equipped with a reduction gear, and is forward and backward by the deceleration output thereof. Pinion gear 247 which is rotationally driven in engagement with the ring gear 248 fixed to the conveyance case 36 of the longitudinal conveyance mechanism 213A in a flange shape, and is carried out by the forward and reverse rotation operation of the electric motor 246. The entire device 213 is adapted to be driven to drive around the longitudinal support point P. FIG. Thus, the swing position and the height position of the discharge port 240 are moved by the swing of the grain discharging device 213 and the up-down swing of the horizontal conveyance mechanism 213B, and the grain discharge position can be changed arbitrarily.

Next, the transmission structure to the bottom screw 210 which is a driving shaft for driving the grain discharging device 213 will be described.

29 to 32, the support plate 215 provided in the lower portion of the front face of the grain tank 208 has a bracket 250 for bearing bearing the front end of the support shaft 210a in the bottom screw 210. ) Is fixed, and the input case 251 is connected to the front surface of the bracket 250. The input case 251 is equipped with an output bevel gear 252 connected to the support shaft 210a and an input bevel gear 253 engaged therewith, so that the input shaft 254 connected to the input bevel gear 253 is inside the body. It is installed to protrude toward.

The bracket 250 and the input case 251 are connected to the legs 250a and 251a but are connected to each other, and in the space formed between the legs 250a and 251a, an eccentric cam having a bearing 255 mounted on an outer circumference thereof. 256 is externally inserted into and fixed to the support shaft 210a of the bottom screw 210. The rotary support shaft 212 of the lower guide plate 211 protrudes forward of the support plate 215, and the operation arm 257 connected to the protruding end thereof is connected to the eccentric cam 256 through the upper and lower long holes 258. Is coupled to the bearing 255. By this structure, the support shaft 210a of the bottom screw 210 is rotated and the eccentric cam 256 is rotated, so that the operation arm 257 coupled to the eccentric cam 256 is the amount of eccentricity of the eccentric cam 256. The reciprocating oscillation with the amplitude according to the above, and the flow guide plate 211 is driven reciprocating oscillation at a predetermined angle so that the grains stored in the tank flow down to the action region of the bottom screw 210 without causing a bridge phenomenon.

A bearing bracket 260 is vertically installed on the gas frame 202 between the grain tank 208 and the engine 204 disposed in front of it, and rotatably mounted and supported on the bearing bracket 260. Engine power is transmitted to the input pulley 261 of a horizontal axis.

As shown in the electric system diagram of Fig. 21, the engine 204 mounted in the transverse direction has a main output shaft 262 that projects toward the inside of the body, and an output shaft 263 for driving the auxiliary machine that projects toward the outside of the body. ), The crawler traveling device 201, the harvesting unit 203 and the threshing device 207 are driven by the power extracted from the main output shaft 262. The output shaft 263 in the outward direction is provided with three output pulleys 264, and the water pump 266 for engine cooling with the transmission belt 265 wound around the output pulley 264, The radiator cooling fan 267 and the generator 268 are driven and a separate transmission belt 269 wound around the output pulley 264 is wound around the input pulley 261. Although not shown, the output pulley 264 can be wound around another transmission belt to drive a compressor for refrigerant compression in an air conditioner equipped with a model of a cabin specification.

In the center of the input pulley 261 subjected to the engine power as described above, an intermediate transmission shaft 271 is slidably inserted into the spline in the axial direction. The intermediate transmission shaft 271 is disposed coaxially with the input shaft 254 supported and bridged to the input case 251, and the intermediate transmission shaft 271 is connected to the input shaft 254 by a spring 272 externally mounted. The slide is being pressed toward. The intermediate transmission shaft 271 and the input shaft 254 are linked to each other via an interlocking clutch 273 at the opposed portion thereof.

The clutch 273 is composed of a boss-shaped clutch member 274 fixedly connected to the distal end of the intermediate transmission shaft 271 and a coupling member 275 formed of a spring pin that penetrates through the distal end of the input shaft 254. And the engagement member 275 of the input shaft 254 is formed at the end diagonal position of the clutch member 274 as shown in FIG. 29 by the clutch member 274 being externally inserted into the distal end of the input shaft 254. 276, which is adapted to transfer power from the intermediate transmission shaft 271 to the input shaft 254.

When the grain tank 208 is pivoted from the grain recovery position to the maintenance position, the engagement member 275 comes out of the clutch member 274 with the movement of the input shaft 254 laterally outward as shown in FIG. The connection between the intermediate transmission shaft 271 and the input shaft 254 is released. On the contrary, when the grain tank 208 is pivoted back from the maintenance position to the original grain recovery position, the engagement member 275 is engaged with the clutch member 274 from the axial direction with the movement in the horizontal direction of the input shaft 254. The intermediate transmission shaft 271 and the input shaft 254 are automatically linked. When the grain tank 208 is pivoted back from the maintenance position to the grain recovery position, the rotational phase of the engagement recess 276 of the clutch member 274 that is stopped rotating and the engagement member 275 of the input shaft 254 are shifted. In such a case, the engagement member 275 contacts and presses the outer end edge of the clutch member 274 so that the intermediate transmission shaft 271 slides back into the body against the spring 272. Next, when the engine 204 is started and the intermediate rotation shaft 271 starts to rotate, the intermediate rotation shaft 271 is moved at the point where the engagement recess 276 of the clutch member 274 has moved to the phase of the coupling member 275. The clutch 273 is pushed in and slides, and the intermediate rotary shaft 271 and the input shaft 254 are brought into interlocking connection automatically.

33 to 35, the direction opening width w of the engaging recess 276 is set to about several times the outer diameter of the engaging member 275 while the depth d of the engaging recess 276 is It is set to the extent which is slightly larger than the outer diameter of the engagement member 275, and the engagement location k with the engagement member 275 in the engagement concave part 276 is formed in the shape which spreads in in the rotation drive direction. In this way, by engaging the coupling concave portion 276 and the coupling member 275 at will, the clutch member 274 is retracted and displaced together with the intermediate transmission shaft 271 by a thrust force generated by a large driving reaction force or the like, thereby engaging the coupling member ( 275) is unavoidably displaced.

Claims (6)

It is a work vehicle provided with the traveling device 1 of the right side and the left side, The steering operation structure is
A first turning mechanism for giving a speed difference to the right and left traveling devices to turn the aircraft;
A second swing mechanism for turning the gas by giving a speed difference greater than that of the first swing mechanism to the right and left traveling devices,
Swing setting means 78 capable of setting a first state in which the first swing mechanism operates or a second state in which the second swing mechanism operates;
An artificially operated steering wheel 77,
With control means 64,
The first swing mechanism so that the speed difference between the right and left traveling devices becomes larger as the control means 64 is operated from the straight position N to the right or the left in the first state. And operate the second turning mechanism so that the speed difference between the right and left traveling devices becomes larger as the steering operation tool 77 is operated from the straight position N to the right or the left in the second state. In what is configured,
In the said 1st state, the unit speed difference by the 1st turning mechanism with respect to the unit operation amount of the said steering operation tool 77 is small in the area | region on the straight position N side of the said steering operation tool, and is the steering limit side of the said steering operation tool. To be larger in the area of,
In the second state, the unit speed difference by the second turning mechanism with respect to the unit operation amount of the steering operation tool 77 is small in the region on the straight position N side of the steering operation tool, and the steering limit side of the steering operation tool is smaller. In the area of
And a change characteristic of the unit speed difference in the first state and a change characteristic of the unit speed difference in the second state are set to different ones. The said 1st and 2nd in Claim 1 so that the unit speed difference of the said 1st state may be smaller than the unit speed difference of a 2nd state in the area | region of the straight position N side of the said steering operation tool 77. A work vehicle characterized by setting a change characteristic of a unit speed difference of a state. The first turning mechanism is a complete turning mechanism 46 for transmitting low-speed power to the other side of the right or left travel device in the same direction as one of the right or left travel devices,
And the second turning mechanism is a brake mechanism (50) for braking the traveling device on the right or left side. The first turning mechanism is a complete turning mechanism 46 for transmitting low-speed power to the other side of the right or left travel device in the same direction as one of the right or left travel devices,
And said second swing mechanism is a reverse rotation mechanism (53) for transmitting power in a reverse direction to one of the right or left travel devices to the other of the right or left travel devices. The first turning mechanism is a complete turning mechanism 46 for transmitting low-speed power to the other side of the right or left travel device in the same direction as one of the right or left travel devices,
The second turning mechanism is a brake mechanism 50 for braking the traveling device on the right or left side,
It is provided with the reverse rotation mechanism 53 which transmits the power of the reverse direction to the one of the traveling device of the right or left to the other of the traveling device of the right or left,
The first state in which the complete swing mechanism 46 is used by the swing setting means 78, the second state in which the brake mechanism 50 is used, and a third state in which the reverse rotation mechanism 53 is used. Configurable,
In the region on the straight position N side of the steering operation tool 77, the unit speed difference in the second and third states is such that the unit speed difference in the second state is smaller than the unit speed difference in the third state. Work vehicle characterized by setting the change characteristic. The first turning mechanism is a complete turning mechanism 46 for transmitting low-speed power to the other side of the right or left travel device in the same direction as one of the right or left travel devices,
The second turning mechanism is a brake mechanism 50 for braking the traveling device on the right or left side,
It is provided with the reverse rotation mechanism 53 which transmits the power of the reverse direction to the one of the traveling device of the right or left to the other of the traveling device of the right or left,
The first state in which the complete swing mechanism 46 is used by the swing setting means 78, the second state in which the brake mechanism 50 is used, and a third state in which the reverse rotation mechanism 53 is used. Configurable,
In the region on the straight position N side of the steering operation tool 77, the unit speed difference of the second and third states is such that the unit speed difference of the second state and the unit speed difference of the third state are the same. Work vehicle characterized by setting the change characteristic.

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