KR101498856B1 - Combine - Google Patents

Abstract

There is provided a work vehicle in which the turning performance of the steering operation structure including the first and second turning mechanisms for imparting a speed difference to the right and left traveling devices and the operability of the turning operation are improved. The unit speed difference by the first turning mechanism (the second turning mechanism) with respect to the unit operating amount of the steering operating member 77 is small in the region on the side of the straight running position N of the steering operating member 77, In the range of the steering angle limit side. The change characteristics of the unit velocity difference in the first state and the change characteristics in the unit velocity difference in the second state are set to be different from each other.

Description

Combine {COMBINE}

The present invention relates to a working vehicle having right and left traveling devices, and more particularly, to a steering operation structure of a working vehicle configured to apply a speed difference to right and left traveling devices to perform a steering operation of a vehicle will be.

As shown in JP2000-335268 A, in the combine which is an example of the work vehicle, speed differences are imparted to right and left traveling devices (1 and 2 in Fig. 1 and 2) and right and left traveling devices, A second turning mechanism (reference numerals 49 and 50 in Fig. 2) for turning the gas by giving a speed difference larger than that of the first turning mechanism to the right and left traveling devices, ).

JP2000-335268 A discloses 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, reference numerals 71 and 55 in Fig. 3, (Reference numeral 58 in Fig. 4).

Thereby, when the steering operation port is operated to the straight-ahead position, the power in the same direction is transmitted to the right and left traveling devices at the same speed, and the gas goes straight.

In the first state, when the steering operating member is operated, for example, to the right, the first turning mechanism is in an operating state, and the gas changes its direction to the right by the speed difference between the right and left traveling devices, The larger the right manipulated variable, the greater the speed difference between the right and left travel devices, and the airframe changes direction to the right with a small turning radius. Also in the second state, when the steering operation member is operated, for example, to the right, the second turning mechanism is in the operating state, and the gas changes direction to the right in the same manner as described above.

JP 2000-335268 A has the first and second turning mechanisms for imparting the speed difference to the right and left traveling devices, there is room for improvement in terms of improvement of the turning performance and the operability of the turning operation.

The present invention relates to a steering operation structure of a work vehicle, which comprises first and second turning mechanisms for imparting a speed difference to right and left traveling devices, wherein a first state in which the first turning mechanism is operated, When the turning condition setting means 78 (in this embodiment, the turning mode switch is started as an example of the turning setting means) capable of setting the second state in which the turning operation of the turning operation is performed is provided, And the like.

In order to attain the above object, the first feature of the present invention is that the steering operation structure is configured as follows.

A first swivel mechanism for imparting a speed difference to right and left travel devices and right and left travel devices to swing the airframe and a second swivel mechanism for imparting a speed difference greater than that of the first swivel mechanism to the right and left travel devices, And a second turning mechanism for pivoting.

A turning setting means capable of setting a first state in which the first turning mechanism operates or a second state in which the second turning mechanism is operated, and a steering operation member that is artificially operated.

In the first state, the first turning mechanism is operated so that the speed difference between the right and left traveling apparatus becomes larger as the steering operating lever is operated from the straight forward position to the right or left, and in the second state, And a control means for operating the second turning mechanism such that the speed difference between the right and left traveling devices becomes larger as the leftward operation is performed.

The unit speed difference by the first turning mechanism with respect to the unit operating amount of the steering operating member in the first state is small in the region on the straight forward position side of the steering operating lever and is large in the region on the steering limit side of the steering operating lever.

The unit speed difference by the second turning mechanism with respect to the unit operating amount of the steering operating member in the second state is smaller in the region on the straight forward position side of the steering operating lever and larger in the region on the steering limit side of the steering operating lever.

The change characteristics of the unit velocity difference in the first state and the change characteristics in the unit velocity difference in the second state are set to be different from each other.

According to the first aspect, in the first state (second state), when the steering operation member is operated to the right (left) side, the first turning mechanism (second turning mechanism) The speed difference between the right and left traveling devices increases as the steering operation port is manipulated largely to the right (left) side by the speed difference of the device, Left direction).

In this case, the speed difference between the right and left traveling devices is relatively small in a state in which the steering operating lever is operated in the region on the straight-ahead position side (the steering operating lever is slightly moved from the straight position to the right or left side) , The gas is relatively gently turned to the right (left) side as compared with the operation of the steering operating member, so that it is suitable for a state of finely adjusting the direction of the gas at the time of straight running. This is particularly suitable for the first state.

Next, the speed difference between the right and left traveling devices becomes relatively large in a state in which the steering operation port is being operated in the area of the steering limit side (the state in which the steering operation port is largely operated from the straight position to the right or left side) The gas is in a state of changing the direction to the right (left) side with a small turning radius as compared with the operation of the operating member, so that it is suitable for a state in which the direction of the gas is rapidly changed. This is particularly suitable for the second state.

According to the first aspect of the invention, the change characteristics of the unit speed difference in the first state and the change characteristics in the unit speed difference in the second state are set to be different from each other.

As a result, the generation state (generation characteristic) of the speed difference between the right and left traveling devices when the steering operation port is operated from the straight ahead position to the steering limit is different in the first and second states, The difference in the turning characteristics between the first and second states is large compared to the case in which the above-described speed difference generation state (generation characteristic) is the same in the two states, 2 state becomes easier to set.

Therefore, in the first and second states, the unit speed difference by the first and second turning mechanisms with respect to the unit manipulated variable of the steering manipulation opening is small in the region on the straight ahead position side of the steering manipulation opening, It is easy to set the appropriate first and second states depending on the state of the work and the work type, and the turning performance of the work vehicle and turning The operability of the operation can be improved.

In the second aspect of the present invention, the change rate of the unit speed difference in the first and second states is set 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- . This is more advantageous in the following points.

In the first state, in the state in which the steering operation port is operated in the region on the straight-ahead position side (the state in which the steering operation port is slightly operated from the straight-ahead position to the right or left side), the speed difference between the right- And the gas is relatively gently turned toward the right (left) side in comparison with the operation of the steering operating member, so that it is suitable for a state of finely adjusting the direction of the gas at the time of straight running.

In this case, according to the second aspect of the invention, since the above-described state is obtained in the first state in which the right and left traveling devices are imparted with a relatively small speed difference to swing the gas, The fine adjustment of the direction of the gas matches the characteristics (the characteristic that the direction of the gas does not change so much), and the driver can finely adjust the direction of the gas at the time of straight running without discomfort.

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

According to the third aspect of the present invention, the first turning mechanism is a grand turn mechanism for transmitting a low-speed power to the other of the right or left traveling apparatus in the same direction as the right or left traveling apparatus , And the second turning mechanism brakes the right or left traveling device.

In the fourth aspect of the present invention, the first turning mechanism is a loose turning mechanism for transmitting a low-speed power to the other of the right or left traveling apparatus in the same direction as the right or left traveling apparatus, Is a reverse rotation mechanism that transmits the power in the opposite direction to the one of the right or left traveling apparatuses to the other of the right or left traveling apparatuses.

When the third feature or the fourth feature is additionally provided in the second feature, a sufficient difference is imparted to the turning characteristics of the first and second states by the clearance turning mechanism, the brake mechanism or the reverse rotation mechanism, And the first and second states are appropriately set depending on the work type.

Therefore, the difference in turning characteristics between the first and second states is large, and the first and second proper states are easily set in accordance with the state of the workpiece and the work type, thereby improving the turning performance of the work vehicle and the operability of the turning operation .

The fifth aspect of the present invention has the following configuration in addition to the second characteristic configuration.

The first turning mechanism is a loose turning mechanism that transmits a low speed power to the other of the right or left traveling apparatus in the same direction as the right or left traveling apparatus and the second turning mechanism is connected to the right or left traveling apparatus It is a brake mechanism that brakes. And a reverse rotation mechanism for transmitting the power in the opposite direction to one of the right or left traveling devices to the other of the right or left traveling devices.

The first state in which the complete turn mechanism is used by the turn setting means, the second state in which the brake mechanism is used, and the third state in which the reverse rotation mechanism is used. The change characteristics of the unit speed differences of the second and third states are set so that the unit speed difference in the second state is smaller than the unit speed difference in the third state in the region on the side of the straight line position of the steering operation port.

According to the fifth aspect of the present invention, since there is a sufficient difference between the turning characteristics of the first, second and third states by providing the loosening mechanism, the brake mechanism and the reverse rotation mechanism, the selection range is broadened according to the state of the work It is easy to set the appropriate first, second, and third states.

In addition, it is preferable that the unit speed difference in the first state is set to be smaller than the unit speed difference in the second state in the region on the side of the straight forward position of the steering operating member, and the unit speed difference in the second state is smaller And the change characteristics of the unit velocity differences in the first, second, and third states are set to be different from each other. As a result, the difference in turning characteristics in the first, second and third states becomes large, and the selection range is widened according to the state of the work and the work type, so that the first, second and third states can be set appropriately.

Therefore, the difference between the first, second, and third states increases the selection width and the first, second, and third states have large differences in turning characteristics. Therefore, , The three states are easily set, and the turning performance of the work vehicle and the operability of the turning operation can be improved.

The sixth characteristic configuration of the present invention has the following configuration in addition to the second characteristic configuration.

The first turning mechanism is a loose turning mechanism that transmits a low speed power to the other of the right or left traveling apparatus in the same direction as the right or left traveling apparatus and the second turning mechanism is connected to the right or left traveling apparatus It is a brake mechanism that brakes. And a reverse rotation mechanism for transmitting the power in the opposite direction to one of the right or left traveling devices to the other of the right or left traveling devices.

The first state in which the complete turn mechanism is used by the turn setting means, the second state in which the brake mechanism is used, and the third state in which the reverse rotation mechanism is used. The change characteristics of the unit speed difference of the second and third states are set so that the unit speed difference of the third state and the unit speed difference of the second state are the same in the region on the side of the straight line position of the steering operation opening.

According to the sixth aspect of the present invention, since a sufficient clearance is provided between the first, second, and third states by providing a complete turn-around mechanism, a brake mechanism, and a reverse rotation mechanism, the selection range is broadened according to the state of the work It is easy to set the appropriate first, second, and third states.

It is also preferable that the unit speed difference in the first state is set to be smaller than the unit speed difference in the second state in the region on the side of the straight forward position of the steering operating member and the unit speed difference between the unit speed difference in the second state and the third state is the same . As a result, the difference in the turning characteristics in the first, second, and third states is not unnecessarily large, and the first, second, and third states are appropriately set according to the state of the work and the work type.

Therefore, the difference in the selection widths in the first, second and third states and the difference in the turning characteristics in the first, second and third states are not unnecessarily large, The states 1, 2, and 3 can be easily set, and the turning performance of the work vehicle and the operability of the turning operation can be improved.

Other features and advantageous features will be apparent from a reading of the following description with reference to the accompanying drawings.

In the following description, unless otherwise specified, the direction in which the combine as an example of the work vehicle advances (advances) forward is referred to as a forward / backward direction, and a horizontal direction perpendicular to the forward / backward direction is referred to as a left / right direction And the direction perpendicular to the longitudinal direction and the lateral direction is referred to as the vertical direction.

The present invention relates to a steering operation structure of a work vehicle, which comprises first and second turning mechanisms for imparting a speed difference to right and left traveling devices, wherein a first state in which the first turning mechanism is operated, The turning performance of the work vehicle and the operability of the turning operation can be improved when the turning condition setting means is provided.

Figs. 1 to 6 are diagrams showing a first embodiment,
Figure 1 is an overall side view of the combine.
2 is a longitudinal front view of the transmission case, right and left transmission cases;
3 is a longitudinal front elevational view of the vicinity of a first swivel mechanism or a grand turn clutch, a second swivel mechanism or a brake mechanism, a second swivel mechanism or a reverse rotation mechanism, and right and left side clutches of a mission case;
4 is a diagram showing a hydraulic circuit structure in an oil pressure unit.
5 is a view showing the relationship between a shift lever, a steering operating member, a turning setting means, an hydrostatic stepless speed changer, and an oil pressure unit.
6 is a graph showing the relationship between the operating position of the steering operating member and the solid line (grand turn) showing the relationship between the operating current of the proportional control valve (the operating pressure of the first turning mechanism or the complete turning mechanism) A solid line (pivot turn) indicating the relationship between the operating current of the valve (the operating pressure of the second turning mechanism or the brake mechanism), the operating position of the steering operating lever and the operating current of the proportional control valve (Spin turn) indicating the relationship between the operating pressure of the tool and the operating pressure of the tool.
Figs. 7 to 16 are views showing the second embodiment,
7 is a side view of the working machine;
8 is a side view of the crawler traveling device.
9 is a plan view of the crawler traveling device.
10 is a side view of the rear portion of the crawler traveling device.
11 is a longitudinal plan view of the crawler tension adjusting device.
12 is a longitudinal side view of the crawler tension adjusting device.
13 is a plan view of the crawler guide installation structure.
14 is a perspective view of the crawler guide mounting portion and the intermediate member.
15 is a plan view of the wheel support;
16 is a side view of the wheel support.
Figs. 17 to 35 are views showing the third embodiment,
17 is an overall side view of the combine.
18 is a side view of the grain tank.
19 is a plan view of the grain tank.
20 is a perspective view of the grain tank as viewed from the inside of the base.
21 is a schematic view of the electric motor system;
22 is a longitudinal side view showing a linkage structure of the bottom screw and the vertical transport mechanism;
23 is an exploded cross-sectional view showing a linkage structure of the vertical transport mechanism and the horizontal transport mechanism;
24 is a rear view of the grain tank.
Fig. 25 is a plan view showing a swivel drive structure of the curvilinear take-out device. Fig.
26 is a rear view showing a carry-out portion of the grain tank;
27 is a perspective view showing a rear portion of the grain tank;
28 is a perspective view showing a state in which the movable cover at the bottom of the grain tank is opened;
29 is a transverse plan view showing a clutch-on state of the electric motor from the engine to the bottom screw;
30 is a cross-sectional plan view showing the clutch-off state of the electric motor from the engine to the bottom screw;
31 is a longitudinal side view showing the transmission structure of the front end portion of the bottom screw;
32 is a front view showing the driving structure of the lower guide plate;
Fig. 33 is a front view of the clutch member viewed from the axial direction; Fig.
34 is a sectional view of the clutch member;
35 is an exploded view showing a coupling recess in the clutch member;

Hereinafter, embodiments of the present invention will be described with reference to the drawings. Although a plurality of embodiments will be described below, it is considered that the combination of the features of one embodiment and the features of the other embodiments is included in the scope of the present invention.

[First Embodiment]

[One]

As shown in Fig. 1, on the front part of the base supported by the crawler traveling device 1 (corresponding to the traveling device) on the right and left sides, the cutting frame 2 is supported so as to be able to ascend and descend around the horizontal axis P1 And an elevating cylinder 3 for elevating and lowering the cutting frame 2 is provided and the preheating part 4 is supported on the cutting frame 2. [ A driving unit 5 is provided on the right side of the front part of the base body, a threshing device 8 is provided on the left side of the rear part of the base body, a grain tank 9 is provided on the right side of the rear part of the base body, Combination of phosphorus demolding is composed.

Next, the mission case 10 will be described.

1 and 2, the mission case 10 is provided near the left and right center of the front part of the base, and a stepped recess 10a is formed on the upper part of the right side of the mission case 10 , And the hydrostatic stepless transmission 11 is connected to the recess 10a of the mission case 10 so as to be inserted therein. The right and left support portions 10b are provided outside the lower portion of the transmission 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, Extended.

As shown in Figs. 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, and the right and left crawler traveling devices 1 Are provided on the right and left ends of the right and left axle cases 15, respectively. A coupling member 10c is provided outside the lower portion of the transmission case 10 and the coupling member 13 is connected to the coupling portion 10c of the transmission case 10 and the transmission case 14 on the right and left sides.

[2]

Next, a description will be given of the structure of a transmission system (linear system) in the mission case 10.

2, the power of the engine (not shown) is transmitted to the input shaft (not shown) of the hydrostatic stepless transmission 11 through a transmission belt (not shown), and the hydrostatic stepless speed change The output shaft 11a of the device 11 is inserted into the interior of the mission case 10. The input shaft 22 is supported on the upper portion of the transmission case 10 so that the transmission gears 23 and 24 are fixed to the input shaft 22 and the output shaft 11a of the hydrostatic stepless transmission 11 is connected to the spline structure And is connected to the transmission gear 24 (input shaft 22).

2, the high-speed gear 25 and the low-speed gear 26 are externally inserted into the transmission shaft 27 supported on the upper portion of the mission case 10 so as to be rotatable relative to each other, The high gear 25, the transmission gear 24 and the low speed gear 26 are meshed with each other and the shift member 28 is integrally rotatably and slidably inserted outside the transmission shaft 27 by a spline structure. The auxiliary speed change device is constituted by the transmission gear 23 and the high speed gear 25, the transmission gear 24 and the low speed gear 26 and the shift member 28. The shift member 28 is connected to the high speed and low speed gears 25 and 26, the power of the input shaft 22 is shifted to the high and low second positions (high speed and low speed positions) and transmitted to the transmission shaft 27. Usually, the shift member 28 is slid to a position where it meshes with the high-speed gear 25, and the high-speed position is set.

2 and 3, a transmission shaft 29 is supported on a lower portion of the transmission case 10, a transmission gear 31 is fixed to a left side portion of the transmission shaft 29, The transmission gear 30 is fixed to the left side of the transmission gear 27 and the transmission gears 30 and 31 are engaged with each other. The output gears 32R and 32L on the right and left sides are externally inserted into the transmission shaft 29 so as to be relatively rotatable relative to each other and the right and left meshing portions (right and left side) of the right and left output gears 32R and 32L 33R and 33L are integrally rotatably and slidably inserted into the transmission shaft 29 by a spline structure. The right side clutch 34 is configured between the right side output gear 32R and the right side engaging portion 33R and between the left side output gear 32L and the left side engaging portion 33L is the left side clutch 34).

The transmission shaft 35 is supported on the right and left support portions 10b of the transmission case 10 and the right and left transmission case 14 as shown in Fig. The power transmission gear 36 fixed to the power transmission shaft 35 is meshed with the right and left output gears 32R and 32L and the transmission shafts 35 The transmission gear 37 is fixed. The right and left axles 38 are supported on the right and left transmission case 14 and the right and left axle cases 15. In the right and left transmission cases 14, And a transmission gear 39 fixed to the axle 38 on the left side are engaged with the transmission gear 37. Right and left axles 38 extend to the right and left in the right and left axle cases 15 and the sprockets 1a of the right and left crawler traveling devices 1 Are connected to the right and left ends of the right and left axles 38, respectively.

2, the power of the input shaft 22 is transmitted to the transmission shaft 27, the transmission gears 30, 31, the transmission shaft 29, the right and left side clutches 34 Left and right output gears 32R and 32L, a transmission gear 36, a transmission shaft 35, transmission gears 37 and 39, right and left axles (right and left side gears 33R and 33L) 38 to the crawler traveling apparatus 1 on the right and left sides, and the gas goes straight.

[3]

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

A spline portion 29a is formed on the outer surfaces of the right and left sides of the transmission shaft 29 and the right and left engagement portions 33R and 33L are connected to the spline portion 29 of the transmission shaft 29 And the receiving member 40 is inserted into the spline portion 29a of the transmission shaft 29 so as to be rotatable integrally with the spline portion 29a.

3, a plurality of recesses are arranged along the circumferential direction on the right side and left side engaging portions 33R, 33L on the side of the receiving member 40, and right and left engaging portions 33R The left and right engaging portions 33R and 33L are disposed on the left and right sides of the housing member 40 and the spring 41, And the output gears 32R and 32L 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 the transmitting state, And is transmitted to the right and left crawler traveling apparatuses 1 through the right and left side clutches 34. [

The piston 42 is slidably disposed between the right and left output gears 32R and 32L and the transmission shaft 29 and the piston 42 is engaged with the right and left engagement portions 33R and 33L so that the pistons 42 and right and left engaging portions 33R and 33L rotate integrally with the right and left engaging portions 33R and 33L and the pistons 42 via spring pins (43) is inserted.

3, when hydraulic oil is supplied between the right and left output gears 32R and 32L and the piston 42, the right and left meshing portions 33R and 33L and the piston 42 are urged by the spring 41 The left and right side gears 32R and 32L are slid to the separated side to be in the cut-off state of the right and left side clutches 34. [ When the hydraulic oil is discharged from between the right and left output gears 32R and 32L and the piston 42, the right and left engaging portions 33R and 33L and the piston 42 are moved by the spring 41 to the right and left output The left and right side clutches 34 are brought into a rolling state by being slid to the engagement side of the gears 32R and 32L.

[4]

Next, a description will be given of the structure of the electric system (tachometer) in the mission case 10.

2 and 3, the transmission shaft 44 is supported on the transmission case 10, and the transmission gear 45, which is inserted into the right side portion of the transmission shaft 44 so as to be relatively rotatable, The first turning mechanism 46 or the second turning mechanism 46 is provided between the transmission shaft 44 and the transmission gear 45 so as to engage with the gear portion of the outer peripheral portion of the engaging portion 33R of the first turning mechanism 33R, Or a complete line clutch is started as an example of a complete line turning mechanism). The first turning mechanism or the complete turn-around mechanism (46) is of a frictional multi-plate type, is operated by being supplied with operating oil, and is discharged to the shutoff state.

2 and 3, the transmission clutch case 47 is externally inserted into the transmission shaft 29 to be relatively rotatable, and the transmission gear 48 fixed to the transmission shaft 44 and the rotary clutch case 47, And the transmission gear 47a on the outer peripheral portion of the transmission gear 47 is engaged. The revolving clutch case 47 is configured to be symmetrical in the left and right directions and the right and left revolving clutches 49 are provided between the revolving clutch case 47 and right and left output gears 32R and 32L. The right and left revolving clutches 49 are of a friction multi-disc type, and are supplied with operating oil so that they are operated in an electric state. In this case, the right and left rotating clutches 49 are arranged so that the friction plates are pressed against each other, so that the right and left rotating clutches 49 are brought into a semi-conductive state even when the working oil is discharged.

2 and 3, when the first swivel mechanism or the loosening mechanism 46 is operated in the power transmitting state, the power of the power transmission shaft 29 is transmitted to the right engaging portion 33R, 45 as a power source at a speed lower than that of the transmission shaft 29 by rotation in the same direction as the transmission shaft 29 through the first turning mechanism or the loosening mechanism 46, the transmission shaft 44 and the transmission gear 48, And is transmitted to the clutch case 47. When the right or left side clutch 34 is operated in the cutoff state and the right or left turning clutch 49 is operated in the power transmission state, The power is transmitted to the right or left output gears 32R and 32L.

As shown in Figs. 2 and 3, a second swing mechanism or a brake mechanism 50 (in this embodiment, a brake is described as an example of a second swing mechanism or a brake mechanism) at the left side of the transmission shaft 44 . The second turning mechanism or brake mechanism 50 is constituted by a friction multi-plate type, and is supplied with operating oil to be operated in the braking state, and the operating oil is discharged to operate in the released state.

2 and 3, when the second turning mechanism or the brake mechanism 50 is operated in the braking state, the orbiting clutch case 47 is rotated via the transmission shaft 44 and the transmission gear 48, State. The right or left side clutch 34 is operated to the cutoff state and the right or left output clutches 49 are operated to the power transmission state, the right or left output gears 32R and 32L are brought into a braking state.

2 and 3, a transmission gear 51 is fixed to the left side portion of the transmission shaft 27, and a transmission gear 52 is externally inserted into the left side portion of the transmission shaft 44 so as to be relatively rotatable And the transmission gears 51 and 52 are engaged with each other and a second swivel mechanism or a reverse rotation mechanism 53 (the second swivel mechanism or the reverse rotation A reverse clutch is described as an example of the mechanism). The second swivel mechanism or the reverse rotation mechanism 53 is constituted by a friction multi-plate type, and is supplied with operating oil so as to be operated in the electric state, and the operating oil is discharged to operate in the cut-off state.

2 and 3, when the second swivel mechanism or the reverse rotation mechanism 53 is operated in the power transmission state, the power of the transmission shaft 27 is transmitted to the transmission gears 51 and 52, Or transmitted to the orbiting clutch case 47 via the reverse rotation mechanism 53, the transmission shaft 44 and the transmission gear 48 as a rotational power in the direction opposite to the transmission shaft 29. When the right or left side clutch 34 is operated to the cutoff state and the right or left turning clutch 49 is operated to the power transmission state, the rotational power in the opposite direction to the power transmission shaft 29 is transmitted to the right or left output gear 32R , 32L.

[5]

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

The pump 11P of the hydrostatic stepless transmission 11 is shifted from the neutral position N and the neutral position N to the high speed side of the forward F and the high speed side of the reverse R as shown in Fig. And the motor 11M of the hydrostatic stepless speed change unit 11 is configured such that it can be shifted to the high and low second stages. A hydraulic cylinder 59 for operating the swash plate of the pump 11P of the hydrostatic stepless type speed changer 11 and a control valve 60 for operating the hydraulic cylinder 59 for operating the hydraulic oil to the hydraulic cylinder 59 are provided, The shift lever 61 and the control valve 60 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 transmission 11 is placed at a position corresponding to the operating position of the shift lever 61 The swash plate of the suction port 11P is operated.

5, a hydraulic cylinder 62 for operating the swash plate of the motor 11M of the hydrostatic stepless type speed changer 11, an electromagnetic-operated control valve (not shown) for operating the hydraulic cylinder to supply hydraulic oil to the hydraulic cylinder 62 And a shift switch 61a is provided on the grip portion of the shift lever 61 and an operation signal of the shift switch 61a of the shift lever 61 is transmitted to the control means 64 The control device is described as an example of the control means). Thus, by operating the shift switch 61a of the shift lever 61, the control valve 63 is operated by the control means 64, the hydraulic cylinder 62 is operated, and the motor of the hydrostatic stepless transmission 11 And the swash plate of the motor 11M is operated to the high speed and low speed positions.

The rotation setting means 78, the grand turn, the pivot turn, and the spin turn angle described in [7], [8], [9] The reason that the turn-around setting means 78 can select the complete turn state, the ground turn state and the extensional turning state in the state is that the change-over switch 61a of the shift lever 61 allows the constant- Of the motor 11M of the motor 11M is being operated to the low speed position. When the swash plate of the motor 11M of the hydrostatic stepless speed change unit 11 is being operated by the speed change switch 61a of the shift lever 61 to the high speed position, regardless of the operating position of the turn setting means 78, The turning state is selected.

[6]

Next, the right and left side clutches 34 (right and left engaging portions 33R and 33L), the right and left turning clutches 49, the first turning mechanism or the loosening mechanism 46, A description will be given of the oil pressure unit 57 for operating the swing mechanism or the brake mechanism 50 and the second swing mechanism or the reverse rotation mechanism 53 to operate the hydraulic fluid.

A charge pump (not shown) and a hydraulic pump 56 are connected to the input shaft (not shown) of the hydrostatic stepless speed change unit 11 as shown in Fig. 4, The charge pump and the hydraulic pump 56 are driven by the input shaft, and the operating oil of the charge pump is supplied to the hydrostatic stepless transmission 11. 2 and 3, the oil pressure unit 57 is connected to the outer surface of the left and right side portions of the transmission case 10 and the external pipe 58 (see FIG. 4) from the oil pressure pump 56 is connected to the oil pressure Unit 57 as shown in Fig.

2 and 3, the left end portions of the transmission shafts 29 and 44 pass through the left and right side portions of the transmission case 10 and are inserted into the oil pressure unit 57. The left end portions of the transmission shafts 29 and 44 And a flow passage 29b is provided in the inside of the transmission shaft 29 through right and left side clutches 34 (right and left meshing portions 33R and 33L) and right and left swing clutches 49 . A flow path 44a is provided in the inside of the transmission shaft 44 through the left end of the transmission shaft 44 and the first swivel mechanism or the loosening rotation mechanism 46 and the second swivel mechanism or the reverse rotation mechanism 53 . A second turning mechanism or a brake mechanism 50 is provided at the end of the transmission shaft 44 in the oil pressure unit 57. [

4, a priority control valve 67, a left turn control valve 68, a relief valve 69, an unload valve 70, a proportional control valve 71, A swing switching control valve 72, and pilot operation valves 73 and 74 are provided. An external piping 58 from the hydraulic pump 56 is connected to the hydraulic unit 57 and a plurality of flow paths are formed on the connecting surface (mating surface) between the hydraulic unit 57 and the left- Right and left swivel control valves 67 and 68, a relief valve 69 and an unload valve 70 are connected to a connecting surface (a fitting surface) Through the flow path of the fuel gas. A drain passage is formed on the connecting surface (mating surface) between the oil pressure unit 57 and the left and right side portions of the mission case 10 and the operating fluid of the relief valve 69 and the unloading valve 70 flows through the above- And returned to the mission case 10.

As shown in Fig. 2, the priority control valve 67 is connected to the right side clutch 34 (right side engaging portion 33R (right side) via the oil passage of the connection surface (mating surface) and the oil passage 29b of the transmission shaft 29 ) And the revolving clutch 49 on the right side. The left turn control valve 68 is connected to the left side clutch 34 (left side engaging portion 33L) and the left side turning clutch 33 (left side engaging portion) through the flow path of the connecting surface (mating surface) (Not shown).

The right and left swing control valves 67 and 68 are configured to be electromagnetically manipulable by the supply positions 67a and 68a and the discharge positions 67b and 68b and the discharge positions 67b and 68b ). The unloading valve 70 is configured to be electromagnetically operable by the shutoff position 70a and the discharge position 70b, and is pressed to the shutoff 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 the right and left swing control valves 67 and 68 and the flow path 29b of the transmission shaft 29 And the swing switching control valve 72 is connected to the first swing mechanism or the relieving mechanism 46 and the second swing mechanism via the oil passage of the connecting surface (mating surface) and the oil passage 44a of the transmission shaft 44, And the swing switching control valve 72 is connected to the second swing mechanism or the brake mechanism 50 through the oil passage 76 of the oil pressure unit 57. [

As shown in Fig. 4, the proportional control valve 71 is constituted by an electromagnetically operated type so that flow rate control (pressure control) of the operating oil is possible. The swing switching control valve 72 is formed in a pilot operated type that can be operated by the complete turn position 72a, the stop position 72b and the extension position 72c and is pushed by the complete turn position 72a. The pilot operated valve 73 is configured to supply the pilot operated oil branched from the oil passage 75 to the swing switching control valve 72 to be operated to the trip position 72b, The pilot operation valve 74 is configured to be supplied to the switching control valve 72 and operated to the extension pivot position 72c.

The right and left swing control valves 67 and 68, the unloading valve 70, the proportional control valve 71 and the pilot control valves 73 and 74 are described in the following sections [7], [8], [9] As shown in Fig.

[7]

Next, a description will be given of a rectilinear state by the steering operation opening 77 (the steering lever is described as an example of the steering operation opening in this embodiment).

The steering operation member 77 is provided on the operation unit 5 (Fig. 1) and the operation position of the steering operation member 77 is controlled by the control unit 64 And the steering operating member 77 is configured to be operable by the straight forward position N, the first pivot positions R1 and L1 on the right and left sides, and the second pivot positions R2 and L2 on the right and left sides . The turning position setting means 78 is provided in the operation section 5 and the operating position of the turning setting means 78 is inputted to the control means 64. The turning setting means 78 sets the turning position (Equivalent to the second state), and the extensible pivot position (corresponding to the second and third states).

The right and left swivel control valves 67 and 68 are operated in the forward and reverse directions when the steering operating member 77 is operated to the straight forward position N regardless of the operating position of the swivel setting means 78 as shown in Figs. The unloading valve 70 is operated to the discharge position 70b and the right and left side clutches 34 (the right and left engaging portions 33R and 33L) are operated to the discharge positions 67b and 68b, The right and left side clutches 34 (right and left engaging portions 33R and 33L) are operated in the transmission state and the right and left side clutches 34 49) is operated in a state of inversion. The first swivel mechanism or the complete turn-around mechanism 46 and the second swivel mechanism or the reverse rotation mechanism 53 are operated in the cut-off state by the proportional control valve 71 and the second swivel mechanism or the brake mechanism 50 is disengaged .

As a result, the power of the input shaft 22 is transmitted to the transmission shaft 27, the transmission gears 30 and 31, the transmission shaft 29, the right and left side gears 29 and 31, The clutch 34 (right and left engaging portions 33R and 33L), the right and left output gears 32R and 32L, the transmission gear 36, the transmission shaft 35, the transmission gears 37 and 39, Is transmitted to the right and left crawler traveling apparatus 1 via the right and left axles 38, and the gas goes straight.

[8]

Next, the state of complete turning by the steering operation tool 77 will be described.

4 and 5, when the turn setting means 78 is operated to the complete turn position, the pilot control valves 73 and 74 operate the turn control valve 72 to the complete turn position 72a . Thereby, when the steering operation member 77 is operated to the first pivotal position R1 on the right side, the priority control valve 67 is operated to the supply position 67a and the unloading valve 70 is operated to the shutoff position 70a, And the operating oil is supplied to the right side clutch 34 (right meshing portion 33R) and the right side swing clutch 49 so that the right side clutch 34 (right side engaging portion 33R) And the right side turning clutch 49 is operated to the electric state.

In this case, as shown in Figs. 2 and 3, since the left clutch SW4 is in the inverted state, the power of the left side clutch 34 (left engaging portion 33L) is transmitted to the left output gear 32L And is transmitted to the output gear 32R on the right side through the right side turning clutch 49 (electric state) from the left side turning clutch 49 A power slightly lower than the power transmission shaft 29 is transmitted to the right output gear 32R. As a result, the gas gently changes direction to the right.

As shown in Figs. 4 and 5, when the steering operation member 77 is operated to the right first pivotal position R1, the priority rotary control valve 67 is operated to the supply position 67a as described above The unloading valve 70 is operated to the shutting position 70a and at the same time the first swing mechanism or the relief rotation mechanism 46 is rotated through the proportional control valve 71 and the swing switching control valve 72 As the steering operating member 77 is operated from the first pivotal position R1 on the right side to the second pivotal position R2 on the right side, the first swivel mechanism 71 is operated by the proportional control valve 71, 6, the operation position of the steering operation member 77 and the operation current of the proportional control valve 71 (the first turning mechanism or the complete turn-around mechanism And the operating pressure of the mechanism 46).

As shown in Figs. 2 and 3, the operating pressure of the first swing mechanism or the relief mechanism 46 is raised by the proportional control valve 71 based on the operating position of the steering manipulation tool 77, The power of the transmission shaft 29 is transmitted to the right engaging portion 33R, the transmission gear 45, the first swivel mechanism or the loosening rotation mechanism 46, the transmission shaft 44, the transmission gear 48, The power of lower speed than that of the transmission shaft 29 is transmitted to the right output gear 32R by the rotation in the same direction as that of the transmission shaft 29 through the right clutch 47 and the right clutch 49. [

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 first turning mechanism or the loosening mechanism 46 simultaneously The operating pressure of the first swing mechanism or the loosening mechanism 46 is lower than the range of the low pressure (the steering operation port 77 is located near the first pivotal position R1 on the right side) The power from the left side clutch 34 (the left engaging portion 33L) is transmitted to the left side clutch 34 (the left side clutch 34) by the power from the first turning mechanism or the loosening mechanism 46, The right side output gear 32R is driven by the power from the left side engaging portion 33L, and the gas gently changes direction to the right side.

Next, when the steering operation member 77 is operated from the first pivotal position R1 on the right side to the second pivotal position R2 side on the right side and the operating pressure of the first turning mechanism or relief mechanism 46 is slightly increased 2 and 3, the power from the first turning mechanism or the loosening mechanism 46 is transmitted from the left side clutch 34 (the left engaging portion 33L) Or the right output gear 32R is driven by the power from the loose return mechanism 46. [ In this state, the output gear 32R of the right side is driven by the power from the left side clutch 34 (the left engaging portion 33L) The output gear 32R of the right side is driven at a low speed by the power of the right hand gear 32R and the right hand side of the output gear 32R is driven at a low speed. The turning radius of the base becomes smaller as it is operated toward the turning position R2.

4 and 5, when the steering operation member 77 is operated to the left first pivotal position L1, the left-turn control valve 68 is operated to the supply position 68a, and the unloading valve 70 are operated to the cut-off position 70a and the operating oil is supplied to the left side clutch 34 (the left engaging portion 33L) and the left swivel clutch 49 so that the left side clutch 34 And the left swivel clutch 49 is operated to the power transmission state. Simultaneously, the same operation as described above is performed, and the gas gently changes direction to the left. When the steering operation member 77 is operated from the first pivotal position L1 on the left side to the second pivotal position L2 on the left side, the same operation as described above is carried out, and the gas turns to the left side.

[9]

Next, the state of the ground pivoting by the steering operation tool 77 will be described.

4 and 5, when the turning setting means 78 is operated to the ground position, the pilot control valves 73, 74 operate the turning control valve 72 to the ground position 72b . Thereby, when the steering operation member 77 is operated to the first pivotal position R1 on the right side, the priority control valve 67 is operated to the supply position 67a and the unloading valve 70 is operated to the shutoff position 70a, And the hydraulic oil is supplied to the right side clutch 34 (right side engaging portion 33R) and the right side swing clutch 49 so that the right side clutch 34 (right side engaging portion 33R) And the right side turning clutch 49 is operated to the electric state. In this case, since the left swivel clutch 49 is in the inverted state, the gas gently changes direction to the right similarly to the preceding [8].

4 and 5, when the steering operation member 77 is operated to the first pivotal position R1 on the right side, the priority control valve 67 is operated to the supply position 67a as described above, The valve 70 is operated to the shutting position 70a and the second swing mechanism or the brake mechanism 50 is operated via the proportional control valve 71 and the swing switching control valve 72 (the pivot position 72b) As the steering operating member 77 is operated from the first pivotal position R1 on the right side to the second pivotal position R2 on the right side, the proportional control valve 71 causes the second turning mechanism The operating position of the steering operating member 77 and the operating current of the proportional control valve 71 (the second turning mechanism or the brake mechanism 50 (see FIG. 6) ) (See the solid line A2 (state of the pivoting state)).

The operating pressure of the second turning mechanism or the brake mechanism 50 is stepped up by the proportional control valve 71 on the basis of the operating position of the steering operating member 77 as shown in Figs. 2 and 3, The braking force is applied to the right output gear 32R through the coaxial shaft 44, the transmission gear 48, the swing clutch case 47 and the right swing clutch 49 to increase the braking force.

2 and 3, the power from the left side clutch 34 (the left engaging portion 33L) and the braking force of the second turning mechanism or the brake mechanism 50 are simultaneously applied to the right side The operating pressure of the second swing mechanism or the brake mechanism 50 is transmitted to the output gear 32R of the first swing position 32R , The power from the left side clutch 34 (the left engaging portion 33L) is increased by the braking force of the second turning mechanism or the braking mechanism 50 and is transmitted to the left side clutch 34 And the output gear 32R on the right side is driven by the power from the sun gear 33L. Thus, when the operating pressure of the second swing mechanism or the brake mechanism 50 is in the low pressure range, the gas gently changes direction to the right.

Next, when the steering operation member 77 is operated from the first pivotal position R1 on the right side to the second pivotal position R2 side on the right side and the operating pressure of the second turning mechanism or brake mechanism 50 is slightly raised 3, the braking force of the second turning mechanism or the braking mechanism 50 is increased by the power from the left side clutch 34 (the left engaging portion 33L) and the second turning mechanism or brake The output gear 32R on the right side is brought into a braking state by the braking force of the mechanism 50 and the base body is pivoted to the right side and as the steering operating member 77 is operated toward the second pivotal position R2 on the right side, The turning radius becomes smaller.

The left turn control valve 68 is operated to the supply position 68a when the steering operating member 77 is operated to the left first pivotal position L1 as shown in Figs. 4 and 5, and the unloading valve 70 And the hydraulic oil is supplied to the left side clutch 34 (the left engaging portion 33L) and the left side swing clutch 49 so that the left side clutch 34 (left side) The engaging portion 33L) is operated to the cut-off state, and the left-hand rotating clutch 49 is operated to the electric state. Simultaneously, the same operation as described above is performed, and the gas gently changes direction to the left. When the steering operating member 77 is operated from the first pivotal position L1 on the left side to the second pivotal position L2 on the left side, the same operation as described above is performed, and the gas is pivoted to the left.

As shown in Figs. 4 and 5, a steering switch 77a is provided at the grip portion of the steering manipulation opening 77. Fig. The turning operation means 77 is operated from the first turning position R1 (L1) on the right (left) side to the right turning position (left) from the turning position setting means 78 as described in the preceding paragraph [ , It is assumed that it is necessary to turn to a smaller radius in the right turn state or the left turn state operated by the second turning position R1 (L1) on the left side.

In this case, as shown in Figs. 4 and 5, when the steering operation member 77 is moved from the first pivot position R1 (L1) on the right (left) side to the second pivot position R1 When the steering switch 77a of the steering manipulation tool 77 is depressed in the state in which the steering control lever 72 is operated with the steering wheel turning position 72a and the steering wheel turning position 72b, Turn to the right (left) side. This state is only while the steering switch 77a of the steering operating lever 77 is being pressed and when the hand is released from the steering switch 77a of the steering operating lever 77 and is returned, 72 is operated from the stop position 72b to the complete turn position 72a, and the gas returns to the complete turn state.

* [10]

Next, a pickup pivotal state by the steering operation tool 77 will be described.

4 and 5, when the swivel setting means 78 is operated to the extensible swivel position, the swivel switch control valve 72 is moved to the swivel swivel position 72c by the pilot operated valves 73, 74 . Thereby, when the steering operating member 77 is operated to the right first pivoting position R1, the priority control valve 67 is operated to the supply position 67a and the unloading valve 70 is operated to the shutoff position 70a The operating oil is supplied to the right side clutch 34 (right side engaging portion 33R) and the right side rotating clutch 49 so that the right side clutch 34 (right side engaging portion 33R) In this case, since the left swing clutch 49 is in the inverted state, the vehicle gently changes its direction to the right in the same manner as in [8].

4 and 5, when the steering operation member 77 is operated to the first pivotal position R1 on the right side, the priority control valve 67 is operated to the supply position 67a as described above, The valve 70 is operated to the shutoff position 70a while the second swivel mechanism or the reverse rotation mechanism 53 is operated through the proportional control valve 71 and the swivel switching control valve 72 (the extension pedal position 72c) And as the steering operating member 77 is operated from the first pivotal position R1 on the right side to the second pivotal position R2 on the right side, the proportional control valve 71 causes the second turning mechanism The operating position of the steering operating member 77 and the operating current of the proportional control valve 71 [the second turning mechanism or the reverse rotation The operating pressure of the mechanism 53)} (see the solid line A3

As shown in Figs. 2 and 3, the operating pressure of the second swing mechanism or the reverse rotation mechanism 53 is increased by the proportional control valve 71 based on the operating position of the steering operating member 77 The power of the electric power transmission shaft 27 is transmitted to the transmission gears 51 and 52 through the second gear mechanism or the reverse rotation mechanism 53, the transmission shaft 44, the transmission gear 48, the orbiting clutch case 47, And is transmitted to the right output gear 32R as a rotational power in the opposite direction to the transmission shaft 29 through the clutch 49. [

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 second turning mechanism or the reverse rotation mechanism 53 are simultaneously The operating pressure of the second turning mechanism or the reverse turning mechanism 53 is lower than the range of the low pressure (when the steering operating member 77 is moved to the vicinity of the first turning position R1 on the right side , The power from the left side clutch 34 (the left engaging portion 33L) is transmitted from the second turning mechanism or the reverse rotation mechanism 53 to the left side clutch 34 And the right output gear 32R is driven by the power from the left-side engaging portion 33L. Thus, when the operating pressure of the second swivel mechanism or the reverse rotation mechanism 53 is in the low pressure range, the gas gently changes direction to the right.

Next, when the steering operation member 77 is operated from the first pivotal position R1 on the right side to the second pivotal position R2 on the right side and the operating pressure of the second pivoting mechanism or the reverse rotation mechanism 53 is slightly increased The power from the second swivel mechanism or the reverse rotation mechanism 53 is transmitted to the second swivel mechanism 34 by the power from the left side clutch 34 (the left engaging portion 33L) Or the output gear 32R on the right side is driven by the power from the reverse rotation mechanism 53. [ In this state, the right output gear 32R is driven in the reverse direction with respect to the left output gear 32L so that the base body is pivotally extended to the right, and the steering operation port 77 is rotated to the right second swivel position R2 ), The turning radius of the gas becomes smaller.

4 and 5, when the steering operation member 77 is operated to the left first pivotal position L1, the left-turn control valve 68 is operated to the supply position 68a, and the unloading valve 70 are operated to the cut-off position 70a and the operating oil is supplied to the left side clutch 34 (left side engaging portion 33L) and the left side swing clutch 49 so that the left side clutch 34 And the left swivel clutch 49 is operated in the power transmission state. At the same time, the same operation as described above is performed, and the gas gently changes direction to the left. When the steering operation member 77 is operated from the first pivotal position L1 on the left side to the second pivotal position L2 on the left side, the same operation as described above is performed, and the gas turns to the left side.

[11]

The operating position of the steering operating member 77 and the operating current of the proportional control valve 71 [Fig. 8], [9], [10] 6), and the relationship between the operating position of the steering operating member 77 and the operating position of the proportional control valve 71 (i.e., the operating position of the first swing mechanism or the loosening mechanism 46) The relationship between the operating current of the steering operating member 77 (the operating pressure of the second turning mechanism or the brake mechanism 50) The relationship between the operating current of the valve 71 (the operating pressure of the second turning mechanism or the reverse rotating mechanism 53) is represented by the solid line A3 (the retracted turning state) in Fig.

The solid lines A1 (completed line turning state), A2 (ground line turning state), and A3 (extension grounding state) are quadratic curves as shown in the following equations B1, B2, B3.

B1 (A1 (completed state)): Y1 = a11 X-X-a21 X + a31

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

B3 (A3 (swing state of revolution)): Y3 = a13 X · X-a23 · X + a33

only

X: the operating position of the steering operation port 77

Y1: The operating current of the proportional control valve 71 (the operating pressure of the first turning mechanism or the relief mechanism 46)

Y2: The operating current of the proportional control valve 71 (operating pressure of the second turning mechanism or the brake mechanism 50)

Y3: The operating current of the proportional control valve 71 (the operating pressure of the second turning mechanism or the reverse turning mechanism 53)

a11 to a33: positive integers

The unit operating current of the proportional control valve 71 with respect to the unit operating amount of the steering operating member 77 (the first turning mechanism or the complete turn driving mechanism 46 ), The unit speed difference generated in the crawler traveling apparatus 1 on the right and left sides by the second pivoting mechanism or the brake mechanism 50 and the second pivoting mechanism or the reverse rotation mechanism 53 (the first and second states Is smaller in the area on the right side and left side first turning positions R1 and L1 side (straight line position N side) of the steering operation opening 77 and the right side and left side And is larger in the region of the first pivotal position R2, L2 side (steering limit side).

In this case, in the positive integers a11 to a33,

a11> a12> a13

a21> a22> a23

a31 > a32 > a33

As shown in Fig. 6, there is a case where the expression B1 [A1 (complete turn state)], the expression B2 [A2 (the ground state)] and the expression B3 [ It is a quadratic curve. As a result, the turning characteristics are different from each other in the complete turn state, the ground state, and the extensional turning state (the change characteristics of the unit speed difference in the first state and the change characteristics in the unit speed difference in the second state are different from each other Equivalent).

The relationship of the positive integers a11 to a33 described above makes it possible to control the area on the right side and left side first turning positions R1 and L1 side (straight line position N side) of the steering operation tool 77 as shown in Fig. The proportional control valve 71 with respect to the unit manipulated variable of the steering manipulation part 77 in the extreme pivot state is set to be larger than the unit manipulated current of the proportional control valve 71 with respect to the unit manipulated variable ) Is small. The unit operation amount of the proportional control valve 71 with respect to the unit operating amount of the steering operating member 77 in the complete running state than the unit operating amount of the proportional control valve 71 with respect to the unit operating amount of the steering operating member 77 in the stand- The current is small.

[First Different Form of the First Embodiment]

(1), (2), and (3) described below are satisfied in the complete line turning state, the ground state, and the extensional turning state of the above-described [first embodiment] It may be configured such that operation of the hydrostatic stepless transmission 11 by the shift switch 61a to the high-speed position of the motor 11M (see [5]) can not be performed.

(1) When the steering operation member 77 is operated between the right and left second pivotal positions R1 and R2 (between the left and right second pivotal positions L1 and L2) State.

(2) When the steering operation port 77 is operated between the first pivotal positions R1 and R2 on the right side (between the first pivotal positions L1 and L2 on the left side and the second pivotal positions L1 and L2 on the left side) And the running speed of the vehicle is higher than the set speed.

(3) When the steering operation port 77 is located at the intermediate position between the first and second pivot positions R1 and R2 on the right side (middle between the first and second left pivot positions L1 and L2 on the left side) Position to the second pivotal position R2 side (left second pivotal position L2 side) from the right side.

[Second alternative form of the first embodiment]

(1), (2), and (3) described below are satisfied in the complete line turning state, the ground state, and the extensional turning state of the above-described [first embodiment] It may be configured such that operation of the hydrostatic stepless transmission 11 by the shift switch 61a to the high-speed position of the motor 11M (see [5]) can not be performed.

(1) The right and left crawler traveling apparatuses 1 are operated by operating the first swivel mechanism or the loosening mechanism 46, the second swivel mechanism or the brake mechanism 50, and the second swivel mechanism or the reverse rotation mechanism 53, In which the speed difference is occurring.

(2) The right and left crawler traveling apparatuses 1 are operated by operating the first swing mechanism or the complete turn-around mechanism 46, the second swing mechanism or the brake mechanism 50 and the second swing mechanism or the reverse rotation mechanism 53, And the running speed of the vehicle is higher than the set speed.

(3) The right and left crawler traveling apparatus 1 are operated by operating the first swivel mechanism or the loosening mechanism 46, the second swivel mechanism or the brake mechanism 50 and the second swivel mechanism or the reverse rotation mechanism 53, And the speed difference is equal to or greater than the set speed difference.

[Third alternative form of the first embodiment]

In the above-described first embodiment, the first different form of the first embodiment and the second different form of the first embodiment, the reverse rotation mechanism 53 is abolished and the first swivel mechanism or the second swivel mechanism It may be constituted so as to include the loosening rotation mechanism 46 and the second turning mechanism or the brake mechanism 50. With this configuration, the loose spin mechanism 46 becomes the first turning mechanism, and the brake mechanism 50 becomes the second turning mechanism.

In the first embodiment of the first embodiment, the first embodiment of the first embodiment and the second embodiment of the first embodiment, the brake mechanism 50 is removed, And a reverse rotation mechanism 53 may be provided. With this configuration, the complete turn-around mechanism 46 becomes the first turning mechanism, and the reverse rotation mechanism 53 becomes the second turning mechanism.

[Fourth alternative form of the first embodiment]

In the first embodiment, the first different form of the first embodiment, and the third different form of the first embodiment described above, the characteristics of the grounding state {expression B2 [A2 (grounding state) (In this case, a12 = a13, a22 = a23, a32 = a33) may be set so that the characteristics of the extensional turning state {the expression B3 [A3

[Fifth alternative form of the first embodiment]

In the above-described first embodiment, the first different form of the first embodiment to the fourth different form of the first embodiment, the formula B1 [Al (completed line state)], the formula B2 [A2 (Linear function) as shown in Fig. 6 by combining a plurality of straight lines (linear functions) having different slopes rather than a quadratic curve as shown in Fig. 6 May be obtained.

[Second Embodiment]

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

In the second embodiment, the crawler tension adjusting device of the crawler traveling apparatus provided with the ground front wheels (124, 125, 126) rotatably disposed on one side of the track frame (122)

A guide member 152 positioned on a lateral side of the track frame 122 on which the grounding rollers 124, 125 and 126 of the track frame 122 are positioned and supported by the track frame 122, A tension adjusting frame 151 which is slidably supported in the forward and backward directions of the track frame and a tension supporting frame 150 rotatably supported on the wheel supporting portion 150 of the tension adjusting frame 151 to support the crawler belt 129, A tension wheel 127 and a tension adjusting mechanism 155 for controlling the tension adjusting frame 151 to slide relative to the guide member 152,

And has a bifurcated shape for supporting the tension wheel 127 on both lateral sides of the wheel supporting part 150. [

The above-described crawler tension device is described, for example, in JP2005-335614 A (paragraph [0019], see Fig. 3).

In the crawler tension adjusting device described in this document, the bracket is inserted into the rear end of the track frame so as to be slidable back and forth, and the tension wheel is pivotally supported on the bracket so as to be freely rotatable.

The tension wheel adjusts the tension of the crawler belt by moving the bracket by screw movement by rotation of the operating shaft.

In this crawler tension adjusting device, a support shaft extending from a bracket to a transverse side is provided, and a tension wheel is supported on an extension end side of the support shaft so that a front wheel for grounding of the track frame is rotated As shown in Fig.

In this crawler tension adjusting device, when a strong tension is generated on the crawler belt, such as when turning, when a large deformation is generated in the support member such as the support shaft of the tension wheel, the operation of the tension wheel is displaced and the crawler belt is easily peeled off . For this reason, it is necessary to firmly support the tension wheel so that the movement of the tension wheel does not occur even when a strong tension is generated on the crawler belt. In the above-described conventional crawler tension adjusting device, the support shaft of the tension wheel is supported only on one side of the tension wheel, and if the support of the tension wheel is rigidly performed, the weight of the support shaft is increased because the support shaft is thick.

On the other hand, according to the configuration of the present embodiment, the guide member 152 located on the side of the ground on which the ground front wheels 124, 125, and 126 of the track frame 122 are positioned is employed, 150 of the track frame 122 so that the crawler belt 129 is properly wound around the tension wheels 127 while being provided with a bifurcate shape for supporting the tension wheels 127 on both lateral sides , 126) is located. As a result, even if 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 adjusting frame 151, etc., Even if a strong tension is generated in the crawler belt 129, the tension wheel 127 can be firmly supported so as to avoid displacement of the operation.

Therefore, it is possible to obtain a crawler tension adjusting device that achieves weight reduction from the surface of the tension wheel support structure while firmly supporting the tension wheel 127 so that the crawler belt 129 is unlikely to be peeled off.

Preferably, the guide member 152 is configured so as to guide the tension adjusting frame 151 in a sliding manner so as to be lifted relative to the track frame 122 as the tension wheel 127 is separated from the guide member 152 . This is advantageous in the following respects.

The tension caused by the tension of the tension wheel 127 on the crawler belt 129 is higher than the tension wheel 127 of the crawler belt 129, And a tension force generated at a portion located lower than the tension wheel 127 and in a direction tilted with respect to the track frame 122 is applied to the tension wheel as 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 changed in a direction along the direction in which the tension adjusting frame 151 is guided and guided by the guide member 152, The tension adjusting frame 151 can be slidably moved while making it difficult for the guide member 152 and the tension adjusting frame 151 to be twisted.

Therefore, the warp between the guide member 152 and the tension adjusting frame 151 is less likely to occur, and a crawler tension adjusting device capable of smoothly and lightly controlling the tension can be obtained.

The tension adjusting mechanism 155 may be 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 across the guide member 152 and the tension adjusting frame 151 It is advantageous in the following respects.

According to this configuration, the tension adjusting mechanism 155 can be operated from the side opposite to the side where the track frame 122 is located with respect to the tension adjusting frame 151 without being disturbed by the track frame 122.

Therefore, it is possible to obtain a crawler tension adjusting device having good operability so that the tension adjusting mechanism 155 can be operated without being disturbed by the operation of the track frame 122, so that the tension can be adjusted comfortably and efficiently.

The track frame 122 is provided with a guide mounting portion 144 for supporting a crawler guide 143 which serves to prevent peeling off of the crawler belt 129. The guide mounting portion 144 is provided with the tension adjusting frame 151 provided on the support portion 144a.

The guide mounting portion 144 has excellent strength because it supports the crawler guide 143. Thus, according to this configuration, the tension adjusting frame 151 can be firmly supported by using the guide mounting portion 144 as a supporting means.

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

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

7 is a side view of a working machine provided with a crawler tension adjusting device A according to the present embodiment. As shown in this drawing, the working machine is constituted by a pair of left and right crawler traveling devices 101 and 101, a traveling vehicle having a driving section equipped with the driving seat 102, And a tensioner 104 connected to the front portion of the base frame 103 of the base frame 103. The tensioner 104 and the graining tank 105 are arranged on the rear side of the base frame 103, Respectively.

This machine harvests rice and barley.

That is, the preloading unit 110 is provided with a cutting frame 111 connected to the front part of the base frame 103 so as to be pivotable up and down. The cutting frame 111 is vertically pivoted by the elevating cylinder 112 A descending operation state in which a grass-diving tool 113 located at the front end portion of the preloading portion 110 is positioned in the transverse direction and descends near the ground, and a lowering operation state in which the minute trellis 113 is elevated from the ground Ascend and descend to the ascending non-working state.

When the traveling body is run with the preloading unit 110 in a descending working state, the preloading unit 110 is provided with a plurality of elevator units 114 arranged in the transversal direction And is introduced into the elevator device 114 corresponding to the minutoregulator 113 and is erected. The erecting process performed by the erecting device 114 is cut by a single cutter type cutting device 115, And the cut-off section from the cut-off device 115 is fed by the feed device 116 to the start end of the threshing feed chain 104a of the threshing device 104. [

The threshing device 104 feeds and supports the underside of the cut-away groove to the back side of the base by the threshing feed chain 104a, and feeds the end of the cut between the cuts to the feed (not shown). The grain tank 105 collects and stores the threshing lips returned from the threshing device 104.

8 is a side view of the crawler traveling apparatus 101 on the left side. 9 is a plan view of the crawler traveling apparatus 101 on the left side. The crawler traveling apparatus 101 on the right side has the same configuration as the crawler traveling apparatus 101 on the left side and the illustration of the crawler traveling apparatus 101 on the right side is omitted. As shown in these drawings, the crawler traveling apparatus 101 includes a track frame 122 connected to the base frame 103 via a pair of support arms 120, 121, A drive rotatable crawler drive wheel 123 supported by the base frame 103 through a transmission case (not shown) at a position above the front side of the track frame 122; 125 and 126 arranged in the front and rear direction of the track frame and supported on the track frame 122 on the side of the track frame 122 and a plurality of ground loops 124, A tension wheel 127 disposed on the rear end of the track frame 122 at a position above the ground front wheel 126 located on the end side and a tension wheel 127 disposed above the track frame 122, A pair of loosely supported back and forth 125 and 126 and the tension wheel 127 and a pair of front and rear carrier rollers 128 and 128. The crawler drive wheels 123 and 123 are rotatable, And a crawler belt 129 made of rubber and rolled up over the crawler belts 129 and 128.

The support arm 120 on the front side includes a rotation support shaft 120a rotatably connected to the base of the support arm 120 and a support shaft 120b for supporting the rotation support shaft 120a And is interlocked with the cylinder rod 131a of the hydraulic cylinder 131 through an interlocking arm 130 integrally rotatably provided at an end opposite to the side to which the arm 120 is connected.

That is, the support arm 120 on the front side is pivoted up and down with respect to the base frame 103 around the central axis of the rotation support shaft 120a by the hydraulic cylinder 131, To / from the base frame (103).

The support arm 121 on the rear side is provided with a rotation support shaft 121a rotatably connected to the base of the support arm 121 and a support arm 121a on the rotation support shaft 121a, And is interlocked with the cylinder rod 133a of the hydraulic cylinder 133 through an interlocking arm 132 integrally rotatably provided at an end opposite to the side to which the hydraulic cylinder 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 through the cancel link 134. [

That is, the support arm 121 on the rear side is pivoted up and down with respect to the base frame 103 around the axis of the rotation support shaft 121a by the hydraulic cylinder 133, The rear end side of the track frame 122 is moved up and down with respect to the base frame 103.

That is, the front and rear support arms 120, 121 of the left and right crawler traveling devices 101, 101 are pivoted, so that the traveling vehicle is inclined in the transverse direction or the back and forth direction with respect to the ground.

That is, the pair of front and rear support arms 120, 121 on one side of the left and right crawler traveling apparatuses 101 are moved upward or downward so that the front and rear support arms 120, The track frame 122 on one side of the left and right crawler traveling apparatus 101 is raised or lowered in parallel with the gas frame 103 and the one end in the lateral direction of the traveling gas And the grounding point by the crawler traveling apparatus 101 on the other end side is used as a swing support point.

The left and right crawler traveling devices 101 are arranged such that one of the support arms 120 on the front side and the support arms 121 on the rear side in the left and right crawler traveling devices 101 move upward or downward, The track frame 122 of the left and right crawler traveling devices 101 is moved to the base frame 103 with the grounding point at the front end side serving as the swing support point by pivoting the support arms 120 and 121 so that the up and down strokes of the support arms 120 and 121 are the same Or vertically swings with respect to the base frame 103 with the grounding point at the rear end side as a swing support point so that one end in the forward and backward direction of the traveling body moves up and down with respect to the ground surface as the swing support point .

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

The rear ground front wheel 125 and the rear ground front wheel 126 are supported so as to be loosely rotatable on the track frame 122 and can not be raised and lowered with respect to the track frame 122. [

The ground front wheel 124 excluding the rear most front wheel 126 and the rear rear wheel 125 among the eight ground front wheels 124, 125, and 126 includes two ground front wheels 124, So that 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 .

As shown in Figs. 9 and 10, each of the above-described balance connecting members 140 is rotatably supported on 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 front wheel group is loosely rotated (rotated) about a portion of the balance connecting member 140 located on the front end side of the connecting shaft 141 And the other grounding front wheel 124 is loosely rotatably supported on a portion of the balance connecting member 140 located on the rear end side of the connecting shaft 141. [

As a result, as the ground front wheel 124 excluding the rear-most front wheel 126 and the rear-rear front wheel 125 among the eight ground front wheels 124, 125, and 126, The front wheels 124 and 124 are provided on the track frame 122 by the balance connecting member 140 and are driven by the oscillation of the balance connecting member 140, (122).

The crawler traveling apparatus 101 includes a crawler guide 142 provided corresponding to each of the front wheels and a crawler guide 143 provided corresponding to the rear ground front wheel 125 and the rear ground front wheel 126 .

As shown in Figs. 8 and 10, the crawler guides 142 corresponding to the front wheel groups are disposed between a pair of left and right guide wheel members of one of the front wheels 124 of the front wheel group, Shaped guide body 142a positioned between a pair of left and right guide wheel bodies of the front ground wheel 124 and a connecting lever 142b connecting the guide body 142a to the balance connecting member 140, 129a of the crawler belt 129 by the guide body 142a to prevent the crawler belt 129 from being peeled off. The crawler guide 142 corresponding to each front wheel group is manufactured by integrally casting the guide body 142a and the connecting lever 142b together with the balance connecting member 140. [

10, the crawler guide 143 corresponding to the rearmost front wheel 126 and the rear wheel front wheel 125 is disposed between the left and right pair of guide wheel body portions of the rear front wheel 125 Shaped guide body 143a positioned between a pair of right and left guide wheel body portions of the last grounding front wheel 126 and a guide mounting portion 144 having the guide body 143a as a track frame 122 The guide body 143a engages with the left and right core bar protrusions 129a of the crawler belt 129 to engage with the crawler belts 129 Thereby preventing peeling. The crawler guide 143 is manufactured by integrally casting the guide body 143a and the connecting lever 143b.

The guide mounting portion 144 of the track frame 122 is constructed by laying a metal block on the lateral side of the track frame 122. The guide mounting portion 144 includes three connecting bolts 145 arranged at the ends of the guide mounting portion 144 in a triangular arrangement in the vertical direction and the back and forth direction of the track frame 122, Thereby supporting the connecting lever 143b.

The crawler traveling device 101 is provided with a crawler tension adjusting device A according to the present embodiment provided at the rear portion of the track frame 122. [

Fig. 9 shows a structure of the crawler tension adjusting device A according to the present embodiment when viewed from a plane. 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 longitudinal 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 drawings, the crawler tension adjusting device A according to the present embodiment includes the tensioning wheel 127, a tension adjusting frame 127 for supporting the tensioning wheel 127 loosely and rotatably in the wheel supporting portion 150, A guide member 152 for supporting the tension adjusting frame 151, a locking portion 153a protruding from the lateral side of the wheel supporting portion 150, And a tension adjusting shaft 155 provided over the support portion 154. [

The tension adjusting frame 151 is provided with the wheel supporting part 150 and a frame body 151a made of a rectangular steel pipe whose one end is connected to the base of the wheel supporting part 150. [

15 is a plan view of the wheel support 150. FIG. 16 is a side view of the wheel support 150. FIG. As shown in these drawings, the wheel support unit 150 includes a pair of shaft support holes 156a and 156a, which are provided on both sides of the tension wheel 127, And a support fork 156. The wheel support portion 150 supports the support shaft 127a of the tension wheel 127 at both lateral 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 lateral side as the lateral side on which the respective ground front wheels 124, 125 and 126 of the track frame 122 are located, And the tension adjusting frame 151 is disposed at a proper position on the transverse side of the track frame 122, that is, at a position where the crawler belt 129 is properly wound around the tension wheel 127 .

The end of the guide member 152 on the side where the tension adjusting frame 151 is projected and the tension adjusting frame 151 are connected to the mounting portion 152 of the track frame 122, And is supported by the support portion 144a from below through a support portion 144a composed of an upper end surface of the support portion 144 and an intermediate member 157 having a lower end portion. The intermediate member 157 includes an upper sheet member 157a and a lower sheet member 157b between the upper sheet member 157a and the support portion 144a, And a lower sheet metal member 157b interposed between the upper and lower plates.

The frame 151a of the tension adjusting frame 151 is slidably supported by the guide member 152 by being slidably inserted in the guide member 152, And is slidably guided by the inner surface of the member 152 to slide in the front-rear direction of the track frame 122. The tension adjusting frame 151 is slid in a state of rising relative to the track frame 122 as the tension wheel 127 is separated from the guide member 152 by setting the sliding direction by the installation direction of the guide member 152 do. That is, the tension adjusting frame 151 is positioned above the tension wheel 127 of the crawler belt 129 and is located at a position lower than the tension wheel 127, And slides along a direction close to the direction of the load applied to the tension wheel 127 by the tension of the portion in the inclined direction 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 adjustment shaft insertion hole provided in the support portion 154 of the guide member 152. When the guide shaft 152 is rotated, The tension adjusting frame 151 is slidably moved with respect to the guide member 152 by moving in the forward and backward direction of the track frame and pushing or pulling the engaging portion 153a of the wheel supporting portion 150. [ The tension adjusting shaft 155 is disposed on the side opposite to the side on which the track frame 122 is located with respect to the tension adjusting frame 151 and extends from the transverse side of the traveling frame of the crawler traveling device 101, It is possible to operate the apparatus without being subjected to an operation failure by the operation of the apparatus.

The crawler tension adjusting device A is configured such that the tension adjusting shaft 155 is rotated by the tension adjusting shaft 155 to slide the tension adjusting frame 151 on the guide member 152 and the intermediate member 157 Move it while guiding it. At this time, the tension adjusting frame 151 slides along the direction close to the direction of the load applied to the tension wheel 127 by the tension of the crawler belt 129, and the tension adjusting frame 151 and the guide member 152 Thereby sliding in a state in which the torsion is less likely to occur. Then, the tension wheel 127 is moved rearward relative to the track frame 122 to push the crawler belt 129 toward the rear side of the traveling device, thereby adjusting the tension of the crawler belt 129 to the increasing side. Alternatively, the tension wheel 127 is moved forward relative to the track frame 122 to reduce the compression of the crawler belt 129, thereby adjusting the tension of the crawler belt 129 to the reduced side.

15 and 16, the wheel supporting unit 150 includes the shaft supporting fork 156 and the engaging part 153a. In addition to the shaft supporting fork 156 and the engaging part 153a, A pair of reinforcing ribs 158 and 158 and a second engaging portion 153b provided on the side opposite to the side where the engaging portion 153a is located with respect to the shaft supporting fork 156. [ The shaft supporting fork 156, the engaging portion 153a, the reinforcing rib 158, and the second engaging portion 153b are integrally cast by casting a lost wax.

The second hooking portion 153b is provided with a tension adjusting shaft 155 when the tension adjusting frame 151 is equipped in the crawler tension adjusting device A of the right crawler traveling apparatus 101. [

[Another embodiment of the second embodiment]

The object of the present invention can be achieved by employing a configuration in which the tension adjusting frame 151 is slidably moved by a grease cylinder instead of the above-described embodiment. Therefore, the tension adjusting shaft 155, the grease cylinder, and the like are generically referred to as a tension adjusting mechanism 155.

[Third embodiment]

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

In the third embodiment, the threshing device 207 and the grain tank 208 are arranged in parallel to the left and right, the engine 204 is arranged in the lateral direction on the front side of the grain tank 208, To the front end of the bottom screw (210) of the tank (208)

An output shaft 263 is protruded from the engine 204 toward the outside of the vehicle and the intermediate transmission shaft 271 is transversely supported and bridged on the front side of the grain tank 208, 271 and the output shaft 263 are connected to each other and the outer side of the intermediate transmission shaft 271 is connected to the front end of the bottom screw 210 in an interlocked manner.

As a gravitational recovery section driving structure of the threshing device, an output shaft provided in a projecting manner in an in-gas direction from an engine disposed in a lateral direction and a gas in-compartment side portion of an intermediate transmission shaft arranged transversely to the front side of the grain tank are wound And the input case provided in the front portion of the grain tank is connected to the intermediate portion of the intermediate shaft so that the engine power is transmitted to the front end portion of the bottom screw through the intermediate transmission shaft and the input case (See, for example, JP 9-205867 A).

In the above conventional structure, since the output shaft protruding from the engine is located at a position farther away from the bottom screw of the grain tank than the bottom screw, the intermediate transmission shaft receiving the engine power is provided to the right and left .

In particular, the gravity tank is configured to be turned around the longitudinal support point of the rear portion to the outside of the gas so as to open the lateral side of the threshing device to a large extent, and the gas outside end of the intermediate transmission shaft and the input portion of the grain tank can be connected / In the case where the input portion of the grain tank is automatically separated from the intermediate transmission shaft by interlocking with the turning opening of the grain tank and the input portion of the grain tank is automatically connected to the intermediate transmission shaft in conjunction with the return turning of the grain tank, It is necessary to support the intermediate portion of the intermediate transmission shaft with a high precision with the other shaft support member so that the long intermediate transfer shaft left on the gas side at the time of opening does not change position. This increases the number of components constituting the transmission structure, There was a tendency.

In contrast, according to the configuration of the present embodiment, since the output shaft 263 protrudes outwardly from the engine 204 even when the engine 204 is disposed inside the gas tank, The inner position of the intermediate transmission shaft 271 and the position at which the intermediate portion of the intermediate shaft 271 is in contact with the front end of the bottom screw 210 can approach the transverse direction of the intermediate transmission shaft 271 ) Is short. The short intermediate transmission shaft 271 needs to be supported in the middle thereof.

Therefore, the transmission structure from the engine 204 to the bottom screw 210 of the grain tank 208 is made compact and simple in the transverse direction while the engine 204 is installed inside the base so that the balance of the weight of the base body is suitable .

Preferably, the grain tank 208 is configured to be pivotable about the longitudinal support point P at the rear, and the input case 251 is connected to the front portion of the grain tank 208, And a clutch 273 disposed concentrically with the input shaft 254 and the intermediate transmission shaft 271 facing the inward side of the internal combustion engine 251 and concentrically opposed to each other. This configuration is advantageous in the following respects.

According to the above configuration, the interlocking of the intermediate transmission shaft 271 and the bottom screw 210 is automatically shut off by turning the grain tank 208 outwardly of the base body, so that it can be largely dropped from the threshing device 207, 207 can be easily performed from the open space. The input shaft 254 receiving the power from the intermediate transmission shaft 271 protrudes from the input case 251 in the in-vivo direction, so that the intermediate transmission shaft 271 can be made shorter.

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

Fig. 17 shows a side view of the whole culm discharging type combine-harvester viewed from the right side of the base. This combine is constructed such that a plurality of ribbed specimens 203 are vertically connected to a front portion of a base frame 202 having a pair of right and left crawler traveling devices 201, A driving unit 206 in which an engine 204 is built in a front portion of the driving unit 206 and a thrashing unit 207 is mounted on the left side of the base frame 202, And a grain tank 208 having a sheet metal structure is provided at a position on the rear side of the driving part 205 on the right side. The curtain cut in the pre-loading part 203 is supplied to the threshing device 207, And the grains picked up by the threshing device 207 are lifted by a screw type grain machine 209 and put into the grain tank 208.

As shown in Figs. 20 and 24, the grain tank 208 is formed in such a shape that the lower portion thereof is narrowed in the front-rear direction, and the grain apparatus 209 is disposed on the left side facing the inside of the gas- A longitudinally long recess 208a is formed. Recesses 208b and 208c are formed on the front and rear sides of the vertically elongated recess 208a to avoid interference with a device portion projecting to the right side surface of the threshing device 207, And an enlarged swelling portion 208d is formed in the upper portion. As described above, by making the left side surface of the grain tank 208 as close as possible to the right side of the threshing device 207, a large tank capacity is ensured.

A bottom screw 210 for delivering the retained curved back to the rear is supported and supported horizontally in the longitudinal direction through the support shaft 210a and the bottom screw 210 is fixed to the lower end of the narrowing portion 208e in the grain tank 208, A flow guide plate 211 having a cross-sectional shape formed in a mountain-like shape is supported and pivotally supported via a rotation support shaft 212.

The narrowing portion 208e of the grain tank 208 is provided with a tilting angle equal to or larger than that of the curved bottom so as to be guided to the bottom screw 210 without leaving the accumulated curl, The lower end of the portion 208a which is narrowed so as to be located on the outer side of the tank 202 is disposed so as to be more laterally outward than the center of the tank lateral width. The lower end of the narrowed portion 208e accommodating the bottom screw 210 is positioned outside the base frame 202 so that the lower end of the portion 208e that is narrowed by the grain tank 208 is positioned on the outer side of the base frame 202 The lower end of the portion 208e of the narrowing of the grain tank 208 can be set lower than that of the upper portion of the tank 208. This makes it possible to increase the tank height (vertical length) It is possible.

In the rear of the grain tank 208, there is provided a screw type curled-up / unloading device 213 for lifting the curled yarn sent out by the bottom screw 210, carrying it laterally and carrying it out of the base. This curled-laying-out device 213 has a screw-type vertical transporting mechanism 213A connected to the lower end of the rear surface of the grain tank 208 and a screw-type vertical transporting mechanism 213A connected to the upper end of the vertical transporting mechanism 213A. Mechanism 213B and the entire curled-laying-out device 213 is capable of turning around a longitudinal support point p concentric with the screw axis of the vertical transport mechanism 213A.

22, a carry-out case 214 for supporting the rear end of the support shaft 210a of the bottom screw 210 is connected to the lower rear end of the grain tank 208, and at the same time, The lower end boss portion 214a of the carry-out case 214 is rotatably fitted and supported in a support portion 202a protruding outwardly in the direction of the vehicle from the longitudinal support point P, And is pivotally supported. 28, a support plate 215 made of a rear plate material is provided on the lower front surface of the grain tank 208. The lower end of the support plate 215 is supported on the upper surface of the base frame 202, The entire weight of the grain tank 208 is supported by the base frame 202 and the support portion 202a at two positions back and forth.

A lock pin 220 is slidably mounted on the support plate 215. The lower end of the lock pin 220 is inserted into the lock hole 222 formed on the side of the base frame 202 so that the lower end of the lock pin 220 is inserted And the lock pin 220 is pulled out from the lock hole 222 against the spring 221 to thereby rotate the grain tank 208 around the longitudinal fulcrum P to rotate the trolley 207 can be moved to a maintenance position in which the right side portion of the door is opened. In addition, the lock pin 220 is pulled up and rotated so as to be retained by the receiving member 223 provided on the support plate 215. [

As shown in Figs. 17 to 19 and Fig. 27, a side cover 225 is fixedly connected to the outside of the lateral side of the grain tank 208 to cover the side surface of the tank. A lower side cover 226 is connected to the lower end of the side cover 225 so as to cover the narrowing portion 208e in the outward direction of the grain tank 208 from the lateral side. The side cover 225 is provided at the rear end of the side cover 225 with the rear side cover 229 covering the bulk of the vertical transport mechanism 213A of the curled- (227) are connected. A vertical frame 231 made of a rectangular pipe is installed upright from the base frame 202 at a rear side position of the vertical transport mechanism 213A and a rear cover 231 covering the vertical transport mechanism 213A from the rear is attached to the vertical frame 231. [ (Not shown). When the grain tank 208 is pivoted transversely outward about the longitudinal fulcrum P, the rear side cover 227, which is pivotally moved in unison with the grain tank 208 as indicated by the imaginary line in Fig. 19, The rear cover 230 does not interfere with the rear cover 230 of the vehicle. 28, a movable cover 232 is mounted on the front end portion of the lower side cover 226 so as to be freely swingable around a longitudinal support point a. By opening the movable cover 232 The lock pin 220 is exposed and the lock operation and the lock release operation of the grain tank 208 can be performed.

The vertical conveying mechanism 213A of the curled-up conveying device 213 is constructed by incorporating vertical conveying screws 236 in a vertical conveying case 235 made of a round pipe material. The lower end of the carrying case 235 is rotatably inserted into and supported around the longitudinal supporting point P with respect to the carrying case 214 as shown in Fig. 22, and at the upper and lower positions of the vertical frame 231 And is supported rotatably by the cylindrical supporting member 237 provided so as to maintain the standing posture of the vertical transport mechanism 213A. The lower end of the support shaft 236a of the vertical transfer screw 236 is inserted into the discharge case 214 and the bevel gear is interlocked with the rear end of the support shaft 210a of the bottom screw 210 And the vertical conveying screw 236 is driven at the same speed as the bottom screw 210.

As shown in FIGS. 22 and 26, in the lower part of the carry-out case 214, the curl sent out by the bottom screw 210 is guided to the conveying region of the vertical conveying screw 236 in the vertical conveying mechanism 213A And the lower surface of the discharge case 214 and the lower surface of the grain tank 208 are formed so that the communication path R extends vertically upward from the upper end of the bottom screw 210, The shape of the outlet port 208f of each of the first and second openings 208a and 205b is formed into a vertically elongated oval shape.

23, the lateral conveying mechanism 213B of the curled-up conveying device 213 is provided with a conveying case 238 made of a round pipe material having the same diameter as the conveying case 235 of the vertical conveying mechanism 213A, And a horizontal feed screw 239 having a support shaft 239a having a diameter larger than that of the support shaft 236a of the vertical feed screw 236 is internally inserted in the feed case 238. On the tip of the feed case 238, A discharge port 240 is provided. An upper end portion of the transport case 235 in the vertical transport mechanism 213A and a base end portion of the transport case 238 in the horizontal transport device 213B are connected and connected to the connection case 241. [ The connection case 241 has an upper end connection case portion 241a fixed to the upper end portion of the transfer case 235 in the vertical transfer mechanism 213A and a lower end connection case portion 241b connected to the base end portion of the transfer case 238 in the horizontal transfer mechanism 213B. And the base end connection case portion 241b is fitted and connected to the upper end connection case portion 241a such that the base end connection case portion 241b is rotatable around the lateral fulcrum Q, (213B) can swing up and down about the transverse fulcrum (Q).

A relay shaft 242 supported on the upper end connection case portion 241a and the base end connection case portion 241b is disposed on the transverse fulcrum Q at both ends. The relay shaft 242 is provided with a feed blade 243 inclined with respect to the transverse fulcrum Q and both ends of the relay shaft 242 are connected to the support shaft 236a of the vertical feed screw 236, And the base end portion of the support shaft 239a of the transverse feed screw 239 is interlocked with the bevel gear at a constant speed. As a result, the vertical conveying screw 236 and the horizontal conveying screw 239 are synchronously driven in conjunction with the rotation of the bottom screw 210, so that the curl sent out from the grain tank 208 is lifted by the vertical conveying mechanism 213A And is horizontally conveyed by the horizontal transport mechanism 213B and discharged from the discharge port 240. [

The relay shaft insertion hole portion of the connection case 241 is formed to have a larger diameter than the transfer case 235 of the vertical transfer mechanism 213A and the transfer case 238 of the horizontal transfer mechanism 213B, Sectional area of the corrugated passage obtained by subtracting the cross-sectional area of the horizontal transport mechanism 213B is set larger than the cross-sectional area of the corrugated passage obtained by subtracting the cross-sectional area of the support shaft in the vertical transport mechanism 213A and the cross- So that the degree of freedom of the curled-up movement in the connection case 241 is increased, so that the curled-up transfer from the vertical transport mechanism 213A to the horizontal transport mechanism 213B is smoothly performed without clogging. A hydraulic cylinder 245 is installed over the upper end connection case portion 241a fixed to the vertical transport mechanism 213A and the transport case 238 of the horizontal transport mechanism 213B, The lateral transport mechanism 213B is driven and oscillated upward and downward within a predetermined range around the transverse shaft Q.

25, an electric motor 246 equipped with a speed reducer is provided in the carry-out case 214 connected to the lower portion of the grain tank 208, and a forward / The pinion gear 247 rotatably driven by the electric motor 246 is engaged with the ring gear 248 fixed to the carrying case 36 of the vertical transport mechanism 213A in a flange shape, So that the entire device 213 is driven and revolved around the longitudinal fulcrum P. The swing position of the discharge port 240 and the height position of the discharge port 240 are moved by the swing of the sweeping device 213 and the vertical swinging of the horizontal transport mechanism 213B so that the sweeping position can be arbitrarily changed.

Next, the transmission structure to the bottom screw 210, which is a driving shaft for driving the curled-laying-out device 213, will be described.

29 to 32, a bracket 250 (not shown) for supporting the front end of the support shaft 210a of the bottom screw 210 is provided on the support plate 215 provided at the lower portion of the front surface of the grain tank 208, And the input case 251 is connected to the front face of the bracket 250. [ The input case 251 is provided with an output bevel gear 252 connected to the support shaft 210a and an input bevel gear 253 engaged with the input bevel gear 252. An input shaft 254 connected to the input bevel gear 253 is connected to the inside As shown in Fig.

The bracket 250 and the input case 251 are connected to each other by legs 250a and 251a and an eccentric cam having a bearing 255 on the outer circumference in a space formed between the legs 250a and 251a. (256) is inserted into and fixed to the support shaft (210a) of the bottom screw (210). The rotation support shaft 212 of the lower guide plate 211 is projected forward of the support plate 215 and the operation arm 257 connected to the projecting end portion of the operation arm 257 of the lower guide plate 211 passes through the upper and lower long holes 258, And is coupled to the bearing 255. With this configuration, the supporting shaft 210a of the bottom screw 210 is rotationally driven to rotate the eccentric cam 256, so that the operating arm 257 coupled to the eccentric cam 256 rotates with the eccentric amount of the eccentric cam 256 And the lower guide plate 211 is reciprocatingly swung at a predetermined angle, so that the curved particles stored in the tank are caused to flow into the action area of the bottom screw 210 without causing a bridge phenomenon.

A bearing bracket 260 is erected on the base frame 202 between the grain tank 208 and the engine 204 disposed in front thereof and is rotatably mounted on the bearing bracket 260. So that the engine power is transmitted to the input pulley 261 having the transverse axial center.

21, a main output shaft 262 protruding toward the inside of the casing and an output shaft 263 for driving an auxiliary machine protruding toward the outside of the casing are provided in the engine 204 mounted in the transverse direction, And the crawler traveling device 201, the preloading portion 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 an output pulley 264 capable of spanning three pulleys 264. An output shaft 264 is wound around the output pulley 264 by a water pump 266 for cooling the engine, The radiator cooling fan 267 and the generator 268 are driven and a separate power transmission belt 269 wound around the output pulley 264 is wound around the input pulley 261. Further, although not shown, another pulley 264 can be wound around the output pulley 264, so that the compressor for compressing the refrigerant in the air conditioning apparatus equipped for the cabin specification type can be driven.

The intermediate transmission shaft 271 is slidably inserted into the spline at the center of the input pulley 261 which receives engine power as described above. The intermediate transmission shaft 271 is disposed coaxially with the input shaft 254 bridged by the input case 251 and the intermediate transmission shaft 271 is connected to the input shaft 254 by an externally inserted spring 272. [ As shown in Fig. The intermediate transmission shaft 271 and the input shaft 254 are connected to each other through a clutch 273 in the mating opposed region.

The clutch 273 is constituted by a boss-shaped clutch member 274 connected and fixed to the distal end of the intermediate transmission shaft 271 and a coupling member 275 formed of a spring pin penetrating the outer periphery of the front end of the input shaft 254 29, the engagement member 275 of the input shaft 254 is engaged with the engaging recess 274 formed at the diagonal position of the end of the clutch member 274, So that power transmission from the intermediate transmission shaft 271 to the input shaft 254 is performed.

When the grain tank 208 is pivoted to the maintenance position from the curled recovery position, the engaging member 275 is disengaged from the clutch member 274 as the input shaft 254 moves outward in the lateral direction as shown in Fig. 30 , The connection between the intermediate transmission shaft 271 and the input shaft 254 is released. Conversely, when the grain tank 208 is returned from the maintenance position to the original rounded position, the engaging member 275 is engaged with the clutch member 274 from the axial direction along with the movement of the input shaft 254 to the inward side The intermediate transmission shaft 271 and the input shaft 254 are automatically and interlockingly connected. The rotational phase of the engaging recess 276 of the clutch member 274 and the engaging member 275 of the input shaft 254 are shifted from each other when the grain tank 208 is returned to the receding position from the maintenance position In this case, the engaging member 275 presses the outer end edge of the clutch member 274 against the intermediate driving shaft 271 so that the intermediate driving shaft 271 slides backward inward against the spring 272. When the engine 204 is started and the intermediate rotation shaft 271 starts rotating, the intermediate rotation shaft 271 is rotated at the point where the engagement concave portion 276 of the clutch member 274 moves to the phase of the engagement member 275 The intermediate shaft 271 and the input shaft 254 are interlocked with each other automatically.

The direction opening width w of the engaging concave portion 276 is set to be several times the outer diameter of the engaging member 275 and the depth d of the engaging concave portion 276 is set to Is formed to have a shape slightly larger than the outer diameter of the engaging member 275 and is formed in such a shape that the engaging portion (k) of the engaging recess 276 with the engaging member 275 penetrates into the engaging recess 276 in the rotational driving direction. The engaging recess 276 and the engaging member 275 are eroded and freely engaged so that the clutch member 274 is retracted together with the intermediate driving shaft 271 by thrust force generated by a large driving reaction force or the like, 275 are shifted freely from each other.

101: Crawler traveling device
122: Track frame
122a: a supporting arm portion, a second supporting arm portion
124, 125, 126: a plurality of ground front wheels
125: After grounding front wheel
126: last ground front wheel
127: Tension wheel
129: Crawler belt
143: Crawler Guide
144: Guide mounting part
151: tension adjusting frame
152: Guide member
155: tension adjusting mechanism
157: intermediate member
157a: upper plate member
157b: the lower sheet member
208 g: inlet
A: Crawler tension adjuster

Claims (7)

The graining device 207 and the grain tank 208 are disposed in parallel on the base frame 202 and the grains collected by the threshing device 207 are passed through the grain tank 208 through the graining device 209, In the combine,
By providing the narrowed portion 208e in the lower portion of the grain tank 208, the grain tank 208 is formed to be narrowed in the front-rear direction,
The graining device 209 is drawn out from the lower portion of the threshing device 207 to the side of the grain tank and then extends upward with respect to the vertical direction so that the graining tank 208 is moved from the upper side to the lower side And the upper longitudinally extending portion 208a of the gravity device 209 is formed so as to overlap the longitudinally extending concave portion 208a in the longitudinal direction in the longitudinal direction, Is inserted into the longitudinally elongated concave portion 208a,
The grain tank 208 is configured so as to be pivotable about the rear longitudinal support point P,
The rear wall portion of the vertically elongated recess 208a is formed as an inclined surface from the inner side to the deep side of the grain tank 208 in plan view,
A front concave portion 208b is formed in front of the lower portion of the vertically elongated concave portion 208a and a rear concave portion 208c is formed at the rear side of the lower portion of the longitudinally long concave portion 208a And,
The width in the lateral direction at the front side of the longitudinally long recessed portion 208a is set wider than the width in the lateral direction at the rear side of the longitudinally long recessed portion 208a in plan view There, combine. The front recess (208b) and the rear recess (208c) are formed such that the recessed volume of the front recess (208b) becomes smaller than the recessed volume of the rear recess (208c) , Combine. The combine according to claim 2, wherein a height of an upper end portion of the front concave portion (208b) is set to be lower than a height of an upper end portion of the rear concave portion (208c). The combine according to claim 2, wherein a width of the front recess (208b) in the gas front-rear direction is set smaller than a width of the rear recess (208c) in the gas front-rear direction. The grain tank (208) according to claim 2, wherein a width of the recessed portion (208b) in the inner side of the grain tank (208) is smaller than a width of the inner side of the grain tank (208) The width of the combine is set smaller than the width of the concave portion. 6. The apparatus according to any one of claims 1 to 5, wherein an inlet port (208g) is formed at an upper portion of the grain tank, an upper end of the grain apparatus (209) is connected to the inlet port (208g)
A portion of the inner surface of the grain tank 208 on the threshing device side that is located forward of the inlet port 208g and rearward of the inlet port 208g bulges toward the threshing device 207 So that the longitudinally long recesses (208a) are formed. 6. The seat belt retractor according to any one of claims 1 to 5, wherein the front concave portion (208b) is provided at a position on the lower side of the longitudinally long recessed portion (208a) in front of the narrowed portion (208e) Is formed adjacent to the lower portion of the vertically elongated concave portion 208a in front and back,
The rear concave portion 208c is formed at a rear portion of the lower portion of the vertically elongated recess 208a and at a position of the upper portion of the narrower portion 208e, And the front and rear sides of the combine.

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