CN101334099A - Working vehicle - Google Patents

Abstract

In order to realize a compact design near a stepless speed change device for operating a gear-box in a traveling drive structure of an operation vehicle, a concave part (10a) depressed from one side of the gear-box (10) to another side thereof is formed, another side of the gear-box (10) is provided with an input shaft (22) of the gear-box (10). The concave part (10a) of the gear-box (10) is provided with the stepless speed change device (11) for traveling, an output shaft (11c) of the stepless speed change device (11) for traveling is connected with the input shaft (22). Another side of the gear-box (10) is provided with driving gears (30, 31) for transmitting power of the input shaft (22) to the downstream side. A drive shaft (29) is supported on the gear-box (10), the power of driving gears (30, 31) are transmitted to the input shaft (22) side of the drive shaft (29) (another side of the gear-box), the concave part (10a) side of the drive shaft (29) is provided with right and left clutches (34).

Description

Operating vehicle

Technical field

The present invention relates to the operating vehicle of a kind of combine-harvester etc.

Background technique

[1]

In the combine-harvester as an example of operating vehicle, for example JP-A-2003-094968 is disclosed like that, stepless speed changes devices and gearbox with the usefulness of advancing.In JP-A-2003-094968, dispose the stepless speed changes devices (Fig. 2 and Fig. 3 9) of the usefulness of advancing at the horizontal sidepiece place on the top of gearbox (Fig. 2 and Fig. 3 8), the output shaft of the stepless speed changes devices of the usefulness of advancing is inserted into the inside of gearbox, be configured in as the input shaft of gearbox (Fig. 2 and Fig. 3 48) gearbox about central authorities.

In JP-A-2003-094968, across about the bottom of gearbox, be supported with transmission shaft (transmission shaft that is supported with the bearing 49 of Fig. 3), the power of the input shaft of gearbox via be configured in gearbox about central authorities driving gear and be delivered to the left and right sides central part of transmission shaft.On the right side of transmission shaft and the left part possess the right side and left side clutch (Fig. 2 and Fig. 3 14), the power of transmission shaft is via the right side and left side clutch and be delivered to the right side and left lateral motion device (Fig. 1 and Fig. 2 1).

Thus, on the right side and left side clutch when being operating as drive state, power is passed to the right side and left lateral motion device, and body directly advances.When right side clutch being operating as dissengaged positions and the left side clutch operating is drive state, body changes direction to the right, with the left side clutch operating is being dissengaged positions and when right side clutch is operating as drive state, and body changes direction left.

[2]

In the combine-harvester as an example of operating vehicle, for example JP-A-2001-054314 is disclosed like that, stepless speed changes devices and gearbox with the usefulness of advancing.In JP-A-2001-054314, the horizontal sidepiece on the top of gearbox (Fig. 1 2) disposes the stepless speed changes devices (M of Fig. 1) of the usefulness of advancing.The output shaft of the stepless speed changes devices of the usefulness of advancing (Fig. 1 1) is inserted into the inside of gearbox, the power of the output shaft of the stepless speed changes devices of the usefulness of advancing is passed to the input shaft (Fig. 1 21) of gearbox via driving gear, the input shaft of gearbox (Fig. 1 21) be configured in gearbox about central authorities.

In JP-A-2001-054314, with transmission of power to the right and left output gear of the right side and left lateral motion device (Fig. 1 4) (Fig. 1 12) be configured in gearbox about central authorities, in the right side and the left side of gearbox, possess freely driving gear of slide is arranged (Fig. 1 11).

Thus, if the slide driving gear (Fig. 1 11) and make itself and driving gear (Fig. 1 27) engagement, then obtain the state of shallowing turn that identical and power low speed of side's direction with the right side or left lateral motion device is passed to the opposing party's (right side or left output gear) of the right side or left lateral motion device.In the state of shallowing turn, for example obtaining, right lateral motion device (right output gear) forward direction is driven, left lateral motion device (left output gear) forward direction is with the driven state of low speed, and body utilization speed difference right and the left lateral motion device is shallowed turn (shallowing turn state) left.

If to opposite direction slide driving gear (Fig. 1 11) and make itself and driving gear (Fig. 1 9) engagement, then obtain the opposing party's's (right side or left output gear) that the power opposite with side's direction of the right side or left lateral motion device is passed to the right side or left lateral motion device inverted status.In inverted status, for example obtaining, right lateral motion device (right output gear) forward direction is driven, the driven state of left lateral motion device (left output gear) direction of drawing back, because the driving direction of the right side or left lateral motion device is opposite, body is to left wheel one positive one anti-pivot turn (wheel one positive one anti-pivot turn state).

[3]

In combine-harvester, as JP-A-2000-335439 is disclosed, swing up and down driving support freely the supporting frame of reaping part (Fig. 1 3), Drive Section (Fig. 1 8), and gearbox (Fig. 2 17) in the configuration abreast on left and right directions of the front portion of body.In JP-A-2000-335439, Drive Section is provided in the right lateral outer side of gearbox, and supporting frame is provided in the opposing party's the lateral outer side in the left side of gearbox.

In JP-A-2000-335439, the speed change of advancing with or the hydraulic mechanism of turning usefulness (Fig. 2 and Fig. 4 23,36) in be contained in the gearbox, by the hydraulic mechanism of operation gearbox, carry out the advance variable speed operation or the operation of turning of body.

[4]

In combine-harvester as an example of operating vehicle, the main transformer speed operation piece that operation main transformer quick-mounting is put and the secondary variable speed operation spare of operation secondary speed-changing device are configured under state arranged side by side respectively in the riding manipulation space (for example, with reference to JP-A-2007-159467 (paragraph [0037] [0041]～[0043], Fig. 2, Fig. 7～Fig. 9)).

Summary of the invention

Problem to be addressed by invention

[1]

The problem of corresponding background technique [1] is as described below.

In JP-A-2003-094968, dispose the stepless speed changes devices of the usefulness of advancing at the horizontal sidepiece place of gearbox, the stepless speed changes devices that becomes the usefulness of advancing is from the horizontal sidepiece of the gearbox outstanding significantly state of side sidelong.Thus, near the compactness of the stepless speed changes devices of the usefulness of advancing in the gearbox this room for improvement is arranged on the one hand.

The objective of the invention is to, in the drive mechanism of advancing of operating vehicle, realize near the compactness of the stepless speed changes devices of the usefulness of advancing in the gearbox.

[2]

The problem of corresponding background technique [2] is as described below.

In JP-A-2001-054314, constitute by the slide driving gear and make the engagement of itself and other driving gear obtain state of shallowing turn and wheel one positive one anti-pivot turn state.But for the driver, the slide general operation of driving gear is heavier, and the engagement of driving gear also is if phase place does not conform to then and can not mesh well, so there is room for improvement the aspect of operability.

Therefore, abolish the slide driving gear and obtained the structure of state of shallowing turn and wheel one positive one anti-pivot turn state, the good structure of following operability has been proposed: possess can with the transmission of power of and low speed identical with side's direction of the right side or left lateral motion device to the right side or the opposing party's of left lateral motion device friction multi-plate shallow turn clutch, and can be, thereby obtain state of shallowing turn and wheel one positive one anti-pivot turn state with the transmission of power opposite to the right side or the multi-plate reversing clutch of the opposing party's of left lateral motion device friction with side's direction of the right side or left lateral motion device.

The objective of the invention is to, in the drive mechanism of advancing of operating vehicle, under the situation of stepless speed changes devices that possesses the usefulness of advancing and gearbox, when in gearbox, possessing the clutch of shallowing turn and reversing clutch, suitably clutch and reversing clutch are shallowed turn in configuration, with near the compactness of the stepless speed changes devices of realizing the usefulness of advancing in the gearbox.

[3]

The problem of corresponding background technique [3] is as described below.

In JP-A-2000-335439, possess and have hydraulic unit (Fig. 4 42) from the control valve (Fig. 4 38,39,41) of row's operation element oil to hydraulic mechanism that give.

The objective of the invention is to, swing up and down driving support freely the supporting frame of reaping part, Drive Section, and gearbox in the front portion of body on left and right directions and in the combine-harvester of row arrangement, in the hydraulic mechanism of speed change usefulness or turning usefulness of will advancing, be contained under the situation in the gearbox, suitably configuration has hydraulic unit from the control valve of row's operation element oil to hydraulic mechanism that give, so that the upkeep operation of hydraulic unit carries out easily.

[4]

The problem of corresponding background technique [4] is as described below.

In the structure in the past shown in the JP-A-2007-159467, two variable speed operation spares are configured in the riding manipulation space under state arranged side by side.

In the riding manipulation space, handle required equipment except also needing the variable speed operation spare to dispose, so equipment disposition is congested, have towards effective utilization in space and carry out room for improvement.

The objective of the invention is to, be conceived to the mode of operation of main transformer speed operation piece and secondary variable speed operation spare, on the configuration structure of two operation piece, work hard, a kind of variable speed operation structure that makes the operating vehicle that the equipment disposition in the riding manipulation space suitably carried out is provided.

Be used to solve the method for above-mentioned problem

[1]

The method that is used to solve problem [1] is as described below.That is, a kind of drive mechanism of advancing of operating vehicle is passed to the right side and left lateral motion device with the power of motor via the stepless speed changes devices and the gearbox of the usefulness of advancing,

Form recess in side's side of above-mentioned gearbox, be equipped with input shaft in the opposing party's side with the gearbox of this recess adjacency,

At the advance stepless speed changes devices of usefulness of above-mentioned recess place configuration, the output shaft of the stepless speed changes devices of this usefulness of advancing is provided in side's side of above-mentioned gearbox,

The output shaft of the stepless speed changes devices of the above-mentioned usefulness of advancing and the input shaft interlock of above-mentioned gearbox are linked,

The driving gear that transmits the power of above-mentioned input shaft is provided in the opposing party's side of above-mentioned gearbox,

Extend up to the opposing party's side from side's side of above-mentioned gearbox and to be provided with transmission shaft, the power of above-mentioned driving gear is passed to this transmission shaft, is equipped with right side clutch and left side clutch to side's lateral deviation of above-mentioned transmission shaft by ground,

The power of the output shaft of the stepless speed changes devices of the above-mentioned usefulness of advancing via above-mentioned driving gear, above-mentioned transmission shaft and the above-mentioned right side and left side clutch, and is passed to the above-mentioned right side and left lateral motion device from the input shaft of above-mentioned gearbox.

This feature is favourable on aspect following.

Fig. 3 and shown in Figure 7 for example is formed with the recess 10a that enters to the opposing party's side (paper right side) in side's side (paper left side) of gearbox 10, disposes the stepless speed changes devices 11 of the usefulness of advancing at the recess 10a place of gearbox 10.Thus, the stepless speed changes devices 11 of the usefulness of advancing becomes the state of the opposing party's side (paper right side) that enters gearbox 10, and the stepless speed changes devices 11 that therefore can not become the usefulness of advancing is from the horizontal sidepiece of the gearbox 10 outstanding significantly state of side sidelong.

According to this feature, for example shown in Figure 7, when forming the recess 10a of gearbox 10, in gearbox 10, input shaft 22 is provided in the opposing party's side (paper right side) with the gearbox 10 of recess 10a adjacency, and driving gear 30,31 also is provided in the opposing party's side (side identical with the input shaft 22 of gearbox 10.The paper right side).Like this, by input shaft 22 and driving gear 30,31 being provided in the opposing party's side (input shaft 22 sides) (paper right side) of gearbox 10, side's side (paper left side) at gearbox 10 is subjected to the influence of input shaft 22 and driving gear 30,31 little, and the recess 10a of gearbox 10 forms easily.

According to this feature, for example shown in Figure 7, the right side and left side clutch 34 in the downstream side that is arranged in driving gear 30,31, be supported with transmission shaft 29 from side's side (paper left side) of gearbox to the opposing party's side (paper right side), the power that constitutes driving gear 30,31 is passed to input shaft 22 1 sides of transmission shaft 29 (above-mentioned the opposing party's side of gearbox.The paper right side), in the recess 10a of transmission shaft 29 side (above-mentioned side's side of gearbox.The paper left side) is equipped with the right side and left side clutch 34.For example shown in Figure 7, when the power that constitutes driving gear 30,31 is passed to input shaft 22 1 sides (paper right side) of transmission shaft 29, produce the allowance on the space in the recess 10a of transmission shaft 29 side (paper left side), therefore can not be equipped with the right side and left side clutch 34 in the recess 10a of transmission shaft 29 side (paper left side) limpingly.

In combine-harvester as an example of operating vehicle, for example shown in Figure 2, how to have Drive Section 5 at the stepless speed changes devices 11 of the usefulness of advancing and the lateral outer side of gearbox 10.In this case, side is outstanding significantly sidelong if the stepless speed changes devices of the usefulness of advancing is from the horizontal sidepiece of gearbox, and the stepless speed changes devices of the usefulness of then advancing sometimes enters Drive Section, sacrifices the space of Drive Section.

With respect to this, in the present invention, the stepless speed changes devices of the usefulness of advancing can not be in from the horizontal sidepiece of the gearbox outstanding significantly state of side sidelong, even therefore constitute the lateral outer side that Drive Section is provided in the stepless speed changes devices and the gearbox of the usefulness of advancing, seldom can sacrifice the space of Drive Section yet.

Thus, in the drive mechanism of advancing of operating vehicle, form the recess that enters to the opposing party's side by side's side at gearbox, and in the recess of gearbox the advance stepless speed changes devices of usefulness of configuration, the stepless speed changes devices that can not become the usefulness of advancing can be realized near the compactness of the stepless speed changes devices of the usefulness of advancing in the gearbox from the horizontal sidepiece of the gearbox outstanding significantly state of side sidelong.

In this case, according to above-mentioned feature, even for example constitute at the stepless speed changes devices of the usefulness of advancing and the lateral outer side of gearbox and be equipped with Drive Section, also seldom can sacrifice the space of Drive Section, therefore easy space with Drive Section is set at big space, can have the various devices in the allowance ground configuration Drive Section, can improve the travelling comfort in the Drive Section.

And, when the recess that side's side is formed with to the right or left the opposing party's side enters of gearbox, by input shaft and driving gear being provided in the opposing party's side (input shaft side) of gearbox, can easily form the recess of gearbox, and can be equipped with the right side and left side clutch not limpingly, based on above-mentioned 2 points, can realize the raising of the productivity of gearbox.

In a preferred embodiment, be equipped with the input shaft of the stepless speed changes devices of the above-mentioned usefulness of advancing, this input shaft is extended to the opposing party's side of above-mentioned gearbox in side's side of above-mentioned gearbox.This feature is favourable on aspect following.

In example state as shown in Figures 7 and 8, the input shaft of stepless speed changes devices 11 of usefulness will be provided as to an opposite side with recess 10a (paper left side) outstandingly if will advance, and the input shaft of stepless speed changes devices 11 that then becomes the usefulness of advancing is from the horizontal sidepiece of the gearbox 10 outstanding significantly state of side (paper left side) sidelong.

With respect to this, according to above-mentioned feature, as example as shown in Figures 7 and 8, the input shaft 11b, 16 of the stepless speed changes devices 11 of the usefulness of advancing is provided in recess 10a side (paper left side), extend to input shaft 22 sides (paper right side), the input shaft 11b, 16 that does not become the stepless speed changes devices 11 of the usefulness of advancing is from the horizontal sidepiece of the gearbox 10 outstanding significantly state of side (paper left side) sidelong.

Thus, since the input shaft of stepless speed changes devices that does not become the usefulness of advancing from the horizontal sidepiece of the gearbox outstanding significantly state of side sidelong, so can realize near the compactness of the stepless speed changes devices of the usefulness of advancing in the gearbox.

[2]

The method that is used to solve problem [2] is as described below.That is, a kind of drive mechanism of advancing of operating vehicle is passed to the right side and left lateral motion device with the power of motor via the stepless speed changes devices and the gearbox of the usefulness of advancing,

Form recess in side's side of above-mentioned gearbox, be equipped with input shaft in the opposing party's side of the gearbox adjacent with this recess,

At the advance stepless speed changes devices of usefulness of above-mentioned recess place configuration, the output shaft of the stepless speed changes devices of this usefulness of advancing is provided in side's side of above-mentioned gearbox,

The output shaft of the stepless speed changes devices of the above-mentioned usefulness of advancing and the input shaft interlock of above-mentioned gearbox are linked,

It is adjacent with above-mentioned recess and extend transmission shaft is set from side's side of above-mentioned gearbox to the opposing party's side,

One side's lateral deviation of the above-mentioned gearbox in above-mentioned transmission shaft is equipped with by ground can to the above-mentioned right side and the mutual direction of left lateral motion device transmission is identical and the friction power that speed is different is multi-plate shallows turn clutch,

The opposing party's lateral deviation of the above-mentioned gearbox in above-mentioned transmission shaft by and be equipped with can be to the multi-plate reversing clutch of friction of the different power of the above-mentioned right side and the mutual direction of left lateral motion device transmission,

The power of the output shaft of the stepless speed changes devices of the above-mentioned usefulness of advancing is delivered to above-mentioned clutch and the reversing clutch of shallowing turn from the input shaft of above-mentioned gearbox.

This feature is favourable on aspect following.

As for example Fig. 3 and shown in Figure 7, be formed with the recess 10a that enters to the opposing party's side (paper right side) in side's side of gearbox 10 (paper left side), dispose the stepless speed changes devices 11 of the usefulness of advancing at the recess 10a place of gearbox 10.Thus, the stepless speed changes devices 11 of the usefulness of advancing becomes the state of the opposing party's side (paper right side) that enters gearbox 10, and the stepless speed changes devices 11 that does not therefore become the usefulness of advancing is from the horizontal sidepiece of the gearbox 10 outstanding significantly state of side sidelong.

Usually, reversing clutch will be opposite with side's direction of the right side or left lateral motion device power to the right or the opposing party of left lateral motion device transmit, transmit bigger moment of torsion (reciprocal power), therefore reversing clutch is constituted friction when multi-plate, need bigger diameter and a plurality of friction plate, reversing clutch becomes than relatively large.

Relative therewith, shallow turn clutch will be identical with side's direction of the right side or left lateral motion device and the power of low speed to the right or the opposing party of left lateral motion device transmit, transmit smaller moment of torsion (power of equidirectional low speed), therefore will shallow turn clutch and constitute friction when multi-plate, need a smaller diameter and a minority friction plate to get final product, shallow turn clutch and become more small-sized.

According to feature of the present invention, for example shown in Figure 7, at and supporting drive shaft 44 adjacent with the recess 10a of gearbox 10, will shallow turn clutch 46 and reversing clutch 53 and be provided under the situation on the transmission shaft 44, be provided in recess 10a one side (above-mentioned side's side of gearbox of transmission shaft 44 with shallowing turn clutch 46.The paper left side), reversing clutch 53 is provided in input shaft 22 1 sides (above-mentioned the opposing party's side of gearbox of transmission shaft 44.The paper right side).

Thus, as for example Fig. 7 and shown in Figure 9, under the situation of the recess 10a that forms gearbox 10, owing to can constitute the clutch 46 of shallowing turn adjacent more small-sized with the recess 10a of gearbox 10, the influence of therefore being shallowed turn clutch 46 is little, and the recess 10a of gearbox 10 forms easily.

Fig. 7 and shown in Figure 9 for example, under the situation that is equipped with reversing clutch 53, be equipped with reversing clutch 53 in the position that the recess 10a from gearbox 10 leaves, even therefore than relatively large reversing clutch 53, influenced by the recess 10a of gearbox 10 and diminish, can be equipped with reversing clutch 53 not limpingly.

In combine-harvester as an example of operating vehicle, for example shown in Figure 2, how to be equipped with Drive Section 5 at the stepless speed changes devices 11 of the usefulness of advancing and the lateral outer side of gearbox 10.In this case, side is outstanding significantly sidelong if the stepless speed changes devices of the usefulness of advancing is from the horizontal sidepiece of gearbox, and the stepless speed changes devices of the usefulness of then advancing enters Drive Section, can sacrifice the space of Drive Section.

With respect to this, according to above-mentioned feature, the stepless speed changes devices that does not become the usefulness of advancing is from the horizontal sidepiece of the gearbox outstanding significantly state of side sidelong, even therefore constitute the lateral outer side that Drive Section is provided in the stepless speed changes devices and the gearbox of the usefulness of advancing, also seldom can sacrifice the space of Drive Section.

Thus, in the drive mechanism of advancing of operating vehicle, by the right or left recess that side's sidepiece forms to the right or left the opposing party's side enters at gearbox, and in the recess of gearbox the advance stepless speed changes devices of usefulness of configuration, the stepless speed changes devices that can not become the usefulness of advancing can be realized near the compactness of the stepless speed changes devices of the usefulness of advancing in the gearbox from the horizontal sidepiece of the gearbox outstanding significantly state of side sidelong.

In this case, according to above-mentioned feature, even for example constitute and be equipped with Drive Section at the stepless speed changes devices of the usefulness of advancing and the lateral outer side of gearbox, also seldom can sacrifice the space of Drive Section, therefore easy space with Drive Section is set at big space, can have the various devices in the allowance ground configuration Drive Section, can improve the travelling comfort in the Drive Section.

And, when the right of gearbox or left side's sidepiece is formed with to the right or the opposing party's side on a left side enters recess, be provided in the recess side of transmission shaft by shallowing turn clutch, reversing clutch is provided in the input shaft side of transmission shaft, can easily form gearbox recess, and can be equipped with reversing clutch not limpingly, based on above-mentioned 2 points, can realize the raising of the productivity of gearbox.

In a preferred embodiment, extend to the opposing party's side from side's side of above-mentioned gearbox the 2nd transmission shaft is set, on the 2nd transmission shaft, possess transmission of power to the right output gear of above-mentioned right lateral motion device and with the left output gear of transmission of power to above-mentioned left lateral motion device, and

Power from above-mentioned input shaft is passed to above-mentioned the 2nd transmission shaft via driving gear, be passed to the above-mentioned clutch of shallowing turn via driving gear from above-mentioned the 2nd transmission shaft, is passed to the right side or left output gear from the above-mentioned clutch of shallowing turn,

The power of above-mentioned input shaft is passed to above-mentioned reversing clutch via driving gear, be passed to the right side or left output gear from above-mentioned reversing clutch.

This feature is favourable on aspect following.

Fig. 7 and shown in Figure 9 for example, when forming the recess 10a of gearbox 10, adjacent with this recess 10a and be equipped with and shallow turn under the situation of clutch 46, according to this feature, via with possess the different transmission shaft 29 of transmission shaft 44 of shallowing turn clutch 46, with the transmission of power of input shaft 22 to shallowing turn clutch 46.

Thus, Fig. 7 and shown in Figure 9 for example, as be called the side's side (paper left side) and the opposing party's side (paper right side) of gearbox 10, even input shaft 22 and shallow turn clutch 46 mutually away from, the power of input shaft 22 can be passed to limpingly via another transmission shaft 29 yet and shallow turn clutch 46.Slightly be equipped with another transmission shaft 29 by recess 10a with leaving, diminish for the influence of the recess 10a of gearbox 10, and the power of input shaft 22 can be passed to limpingly via another transmission shaft 29 and shallow turn clutch 46 from gearbox 10.

For example as Fig. 7 and shown in Figure 9, with the transmission of power of input shaft 22 during to reversing clutch 53, input shaft 22 and reversing clutch 53 are provided in the same side mutually of the opposing party's side (paper right side) that is called gearbox 10, therefore diminished by the influence of the recess 10a of gearbox 10, and the power of input shaft 22 can be passed to reversing clutch 53 limpingly.

Thus, the power of input shaft can be passed to limpingly via another transmission shaft and shallow turn clutch, and the power of input shaft can be passed to reversing clutch limpingly, based on above-mentioned 2 points, design aspect at gearbox can have allowance, can realize the raising of the productivity of gearbox.

In a preferred embodiment, on above-mentioned the 2nd transmission shaft to side's lateral deviation of above-mentioned gearbox by and be equipped with the above-mentioned right side and left output gear,

Be equipped with the transmission of power of above-mentioned input shaft to the driving gear of above-mentioned the 2nd transmission shaft and with the transmission of power of above-mentioned input shaft driving gear in the opposing party's side of above-mentioned gearbox to above-mentioned reversing clutch.

This feature is favourable on aspect following.

As for example Fig. 7 and shown in Figure 9, with the transmission of power of input shaft 10 during to another transmission shaft 29 and reversing clutch 53, according to this feature, in the opposing party's side (input shaft 22 sides of gearbox 10.The paper right side) is equipped with the transmission of power of input shaft 10 to the driving gear 30,31 of another transmission shaft 29, and with the transmission of power of input shaft 10 driving gear 51 to reversing clutch 53.

Like this, by the opposing party's side (input shaft 22 sides at gearbox 10.The paper right side) be equipped with input shaft 22 and driving gear 30,31,51, the side's side (paper left side) at gearbox 10 is diminished by the influence of input shaft 22 and driving gear 30,31,51, and the recess 10a of gearbox 10 forms easily.

Fig. 7 and shown in Figure 9 for example, be equipped with on another transmission shaft 29 transmission of power to the right side and when right and left output gear 32R, the 32L of left lateral motion device, according to this feature, the power that constitutes driving gear 30,31 is passed to input shaft 22 1 sides of transmission shaft 29 (above-mentioned the opposing party's side of gearbox.The paper right side), in the recess 10a of transmission shaft 29 side (above-mentioned side's side of gearbox.The paper left side) is equipped with right and left output gear 32R, 32L.

For example as Fig. 7 and shown in Figure 9, if the power that constitutes driving gear 30,31 is passed to input shaft 22 1 sides of transmission shaft 29, then produce the allowance on the space, therefore can not be equipped with right and left output gear 32R, 32L limpingly in the recess 10a of transmission shaft 29 side (paper left side) in the recess 10a of transmission shaft 29 side (paper left side).

Thus, by input shaft and driving gear being configured in the opposing party's side (input shaft side) of gearbox, the recess of gearbox be can easily form, also can right and left output gear be equipped with limpingly at the recess sidepiece of transmission shaft, based on above-mentioned 2 points, can realize the raising of the productivity of gearbox.

[3]

The method that is used to solve problem [3] is as described below.That is, a kind of combine-harvester,

Dress is advanced in the front portion of body is equipped with, and speed change is used or the gearbox of the hydraulic mechanism of turning usefulness, and,

Drive Section is provided in a lateral outer side of above-mentioned gearbox,

Support another lateral outer side that the supporting frame of reaping part is provided in above-mentioned gearbox freely with swinging up and down driving,

The hydraulic unit that will have the control valve of the row's of giving operation element oil on above-mentioned hydraulic mechanism is provided in the horizontal sidepiece of the supporting frame side of above-mentioned gearbox.

This feature is favourable on aspect following.

Support the supporting frame of reaping part freely swinging up and down driving, Drive Section and gearbox in the front portion of body on left and right directions abreast in the combine-harvester of configuration, usually, reaping part is risen be urged in limited time, reaping part forwards leaves the top from the front portion of body, therefore in an opposite side with Drive Section, open between the front portion of reaping part and body, the worker can enter between the front portion of reaping part and body (for example the JP-A-2000-335439 from an opposite side with Drive Section, right side in the front portion of body possesses Drive Section, left side in the front portion of body possesses reaping part, reaping part is risen be urged to and prescribe a time limit, the worker can enter between the front portion of reaping part and body from the left side of the front portion of body).

If on the right side of for example gearbox or the horizontal sidepiece of the Drive Section side in left side be equipped with hydraulic unit, then the worker is when an opposite side with Drive Section enters between the front portion of reaping part and body, for the worker, hydraulic unit is positioned at the opposite side (Drive Section side) of gearbox, so the upkeep operation of hydraulic unit becomes and is difficult to carry out.

Similarly, if be equipped with hydraulic unit at the front side portion of gearbox, then because reaping part is positioned at the front side of hydraulic unit, the upkeep operation of hydraulic unit becomes and is difficult to carry out.If the rear lateral portion at gearbox is equipped with hydraulic unit, then because the front portion of body is positioned at the rear side of hydraulic unit, the upkeep operation of hydraulic unit becomes and is difficult to carry out.

With respect to this,, be equipped with hydraulic unit at the horizontal sidepiece of the supporting frame side of gearbox according to above-mentioned feature.When the worker entered between the front portion of reaping part and body from an opposite side with Drive Section, for the worker, hydraulic unit was positioned at a side nearby (worker's side) of gearbox, so the upkeep operation of hydraulic unit becomes and carries out easily.

Thus, swing up and down driving support freely the supporting frame of reaping part, Drive Section and gearbox in the front portion of body on left and right directions abreast in the combine-harvester of configuration, when having adorned the hydraulic mechanism of advance speed change usefulness or turning usefulness in gearbox, have and become for the upkeep operation of hydraulic unit of the control valve of row's operation element oil to hydraulic mechanism to carry out easily, can improve the maintainability and the operability of combine-harvester.

In a preferred embodiment, the left and right directions upper support in the inside of gearbox is useful on the transmission shaft of the above-mentioned hydraulic mechanism of supporting, the inside that above-mentioned hydraulic unit is inserted in the end of above-mentioned transmission shaft,

The oil circuit that is equipped with the end from above-mentioned hydraulic mechanism to above-mentioned transmission shaft in the inside of above-mentioned transmission shaft and extends carries out the row's of giving operation of working oil to above-mentioned hydraulic mechanism via above-mentioned oil circuit from above-mentioned hydraulic unit.

This feature is favourable on aspect following.

In the inside of gearbox, hydraulic mechanism is by transmission shaft (Fig. 2 of JP-A-2000-335439 and Fig. 4 20,28) supporting.

From hydraulic unit (control valve) to hydraulic mechanism carry out working oil give row's operation the time, according to above-mentioned feature of the present invention, be equipped with hydraulic unit on the right side of gearbox or the horizontal sidepiece of left supporting frame side, and, carry out the row's of giving operation of working oil to hydraulic mechanism via the oil circuit of transmission shaft from hydraulic unit (control valve) with the inside that hydraulic unit is inserted in the end of transmission shaft.Thus, less needs stride across the pipe arrangement of hydraulic unit (control valve) and hydraulic mechanism configuration effort oil etc., and hydraulic unit (control valve) and hydraulic mechanism can be connected by short path (oil circuit of transmission shaft).

Thus, from hydraulic unit (control valve) to hydraulic mechanism carry out working oil give row's operation the time, can connect hydraulic unit (control valve) and hydraulic mechanism by short path (oil circuit of transmission shaft), be favourable aspect the simplification of structure.

[4]

The method that is used to solve problem [4] is as described below.That is, a kind of speed changing structure of advancing of operating vehicle,

Be provided with comprise can stepless variation capacity the hydraulic type pump, and accept from the working oil of above-mentioned hydraulic type pump and the infinite variable speed main transformer quick-mounting of the energy of driven hydraulic motor is put, being provided with the output variable speed that will put from above-mentioned main transformer quick-mounting is the multistage secondary gear of gear type

The main transformer speed operation piece of change being regulated above-mentioned hydraulic type pump is configured in the riding manipulation space, is configured in outside the riding manipulation space switching the secondary variable speed operation spare of regulating the secondary gear of said gear formula.

This feature is favourable on aspect following.

It is can be infinite variable speed that the main transformer quick-mounting is put, and is used to trickle speed regulation when therefore advancing when operation is advanced and on the road.Therefore, main transformer speed operation piece need be configured in as far as possible the driver near, therefore be configured in the riding manipulation space.

On the other hand, secondary speed-changing device also is used to trickle speed regulation unlike the main transformer quick-mounting is put, and near the necessity that therefore is configured in the driver is little.Therefore secondary variable speed operation spare is configured in outside the riding manipulation space.

Thus, be conceived to the function that main transformer speed operation piece and secondary variable speed operation spare are realized, selected respectively the position be set, so the equipment disposition the riding manipulation space in can complexity, the speed changing structure of advancing of operating vehicle of effective utilization of implementation space can be provided.

In a preferred embodiment, above-mentioned hydraulic motor is constituted volume-variable.

This feature is favourable on aspect following.

According to this structure, in hydraulic motor, can change capacity, therefore in this hydraulic motor, can adopt with the hydraulic type pump that can infinitely change capacity in the different stepped gearing mode of volume-variable mode, also can adopt the mode that can infinitely change capacity.

Thus, can realize the variation of the gear shift mode of main transformer quick-mounting in putting.

About other feature structure and the favourable effect that is realized by its feature structure, reading the following description by the reference accompanying drawing can be clear and definite.

Description of drawings

Fig. 1 is figure that a preferred implementation of the present invention is shown, be unitary side view as the combine-harvester of an example of operating vehicle.

Fig. 2 is near the plan view of gearbox of the front portion of combine-harvester.

Fig. 3 is near the plan view of gearbox of the front portion of combine-harvester.

Fig. 4 is near the side view of gearbox of the front portion of combine-harvester.

Fig. 5 is the side view of gearbox.

Fig. 6 is near the side view of the bottom of gearbox.

Fig. 7 is the vertical profile plan view of gearbox, the right side and Left Drive case.

Fig. 8 is near the vertical profile plan view of the input shaft of hydrostatic formula stepless speed changes devices and gearbox.

Fig. 9 is near the vertical profile plan view of shallowing turn clutch, break, reversing clutch, the right side and left side clutch of gearbox.

Figure 10 is the rear view of the right and left engaging piece in the right side and the left side clutch.

Figure 11 is turning clutch box in the right side and the left-hand bend clutch and the stereogram of accepting parts.

Figure 12 is the figure that the oil hydraulic circuit structure in the hydraulic unit is shown.

Figure 13 is the figure that the relation of main shift lever, deflecting bar, turning motor switch, hydrostatic formula stepless speed changes devices and hydraulic unit is shown.

Figure 14 illustrates the riding manipulation portion of combine-harvester and the plan view of gearbox part.

Figure 15 is the plan view that the riding manipulation portion of combine-harvester is shown.

Figure 16 is the stereogram that the grip part of main shift lever is shown.

Figure 17 is the side view that gearbox is shown.

Figure 18 is the hydraulic circuit diagram of hydrostatic formula stepless speed changes devices.

Figure 19 is the cross-sectional plan view that stopping brake mechanism is shown.

Figure 20 illustrates the cam disk of stopping brake mechanism and the side view of operating arm.

Figure 21 (a) illustrates the vertical profile rear view of stopping brake mechanism at the state of off-position, and Figure 21 (b) illustrates the vertical profile rear view of stopping brake mechanism at the state of on positi.

Figure 22 (a) illustrates the cam disk of stopping brake mechanism under the state of off-position and the action diagram of ball, guide finger, force application spring, and Figure 22 (b) illustrates the cam disk of stopping brake mechanism under the state of on positi and the action diagram of ball, guide finger, force application spring.

Figure 23 is the side view of crawler travel device.

Figure 24 is the plan view of crawler travel device.

Figure 25 is the vertical profile side view of adjusting idler wheel supporting structure.

Figure 26 is the plan view of adjusting idler wheel supporting structure.

Figure 27 makes advance the from high to lower side view of the crawler travel device when mobile of working machine.

Figure 28 is the side view of swing limting mechanism.

Figure 29 is the plan view of swing limting mechanism.

Figure 30 is the side view of the swing boundary of swing track-frame before illustrating.

Embodiment

One preferred embodiment of operating vehicle of the present invention is described based on the combine-harvester (combine-harvester) of an example of operating vehicle with reference to the accompanying drawings.

In addition, short of different expressing, in the following description, the direction of forwards directly advancing (advancing) with the body of advancing of combine-harvester is that benchmark is referred to as fore-and-aft direction, the substantially horizontal vertical with this fore-and-aft direction is called left and right directions (or transverse direction), the direction vertical with fore-and-aft direction and left and right directions is called above-below direction.

[1]

As shown in Figures 1 and 2, in the front portion of the body that is supported by right and left crawler travel device 1, supporting frame 2 is supported freely around transverse axis heart P lifting, possesses the lifting pressure cylinder 3 that lifting drives supporting frame 2, and reaping part 4 is supported on the supporting frame 2.Right side in the front portion of body possesses Drive Section 5, and the downside in the driver's seat 6 of Drive Section 5 has motor 7.Left side at the rear portion of body possesses hulling device 8, possesses cereal box 9 on the right side at the rear portion of body, is constituted as the combine-harvester from off-type (culm head discharging type).

Then, gearbox 10 is described.

As shown in Figures 1 and 2, possessing gearbox 10 near the central authorities about the front portion of body, possessing Drive Section 5 in the right lateral outer side of gearbox 10.Transverse axis heart P is positioned at the rear of the left lateral outer side of gearbox 10, and supporting frame 2 extends to the front side from the position of transverse axis heart P, and supporting frame 2 is positioned at the left lateral outer side of gearbox 10.

As Fig. 3 and shown in Figure 7, gearbox 10 is aluminium die casting systems, constitute two segmenting structures of right side part 10R and left part 10L, outside on the top of the right side of gearbox 10 part 10R is formed with ladder difference shape recess 10a, in plan view (with reference to Fig. 3 and Fig. 7), recess 10a enters near (the paper left side at least) of the connecting part 10b of gearbox 10 (right side and left part 10R, 10L).

As Fig. 3 and shown in Figure 7, hydrostatic formula stepless speed changes devices (HST, it is the example of electrodeless variable-speed device of usefulness of advancing, and be the example that the main transformer quick-mounting is put) 11 be configured to enter the recess 10a of gearbox 10 (right side part 10R), the recess 10a of the oral area block 11a of hydrostatic formula stepless speed changes devices 11 and gearbox 10 (right side part 10R) links.The oral area block 11a of hydrostatic formula stepless speed changes devices 11 goes up to link support unit 12 cylindraceous, and support unit 12 extends to the left, and the arm 12a of support unit 12 and gearbox 10 (left part 10L) link.

As Fig. 3 and shown in Figure 7, possess right support 10c and left support 10c in the outside of the bottom of gearbox 10 (right side and left part 10R, 10L).Possess right transmission case 14 and Left Drive case 14, the right side and Left Drive case 14 extend (with reference to Fig. 4 and Fig. 5) with the right and left support 10c binding of gearbox 10 (right side and left part 10R, 10L) and to the front side.Right and left axle box 15 links with the right side and Left Drive case 14 and reaches the left side extension to the right, and the sprocket wheel 1a that drives right and left crawler travel device 1 is provided in the right side of the right side and left axle box 15 and the end in left side.

Shown in Fig. 3,6,7, outside in the bottom of gearbox 10 (right side part 10R), on the part different of gearbox 10 (right side and left part 10R, 10L), possess linking department 10d is arranged with the right side and left support 10c, to the right side and Left Drive case 14, linking has connected element 13 from the linking department 10d of gearbox 10 (right side part 10R).

[2]

The structure of the transmission system (directly entering system) in the gearbox 10 (right side and left part 10R, 10L) then, is described.

Shown in Fig. 2,3,8, input shaft 16 is supported on the support unit 12, input belt wheel 17 is attached at the end of input shaft 16, and in the inside of support unit 12, the input shaft 11b of hydrostatic formula stepless speed changes devices 21 and input shaft 16 are bonded via linking parts 18.The power of motor 7 is passed to input belt wheel 17 via driving belt 19, and the power of motor 7 is passed to reaping part 4 via driving belt 20 and hydrostatic formula stepless speed changes devices 21.

As shown in Figures 7 and 8, top at gearbox 10 (right side and left part 10R, 10L), input shaft 22 with the recess 10a of gearbox 10 (right side part 10R) mode in abutting connection with (opposed), be supported in the gearbox 10 (left part 10L), driving gear 23,24 is fixed on the input shaft 22 by spline structure.The output shaft 11c of hydrostatic formula stepless speed changes devices 11 is inserted into the inside of gearbox 10 (right side and left part 10R, 10L), links with driving gear 24 (input shaft 22) by spline structure.

As shown in Figures 7 and 8, high gear 25 and low speed gear 26 rotate on the outer freely transmission shaft 27 that is embedded in the top that is bearing in gearbox 10 (right side and left part 10R, 10L) relatively, driving gear 23 and high gear 25, driving gear 24 and low speed gear 26 engagements, shift component 28 is by rotation of spline structure one and outer sliding freely being embedded on the transmission shaft 27.Thus, utilize driving gear 23 and high gear 25, driving gear 24 and low speed gear 26, shift component 28 to constitute as the secondary gear A of the gear type of secondary speed-changing device, by making shift component 28 and high speed and low speed gear 25,26 engagements, the power of input shaft 22 is passed to transmission shaft 27 by speed change for height two-stage (high speed and low-speed position).Usually, shift component 28 by slide to high gear 25 position engaged, be set to high speed position.

As Fig. 7 and shown in Figure 9, be supported with transmission shaft 29 across the bottom of gearbox 10 (right side and left part 10R, 10L), be fixed with driving gear 31 near the left side of transmission shaft 29 (internal surface of the wall portion of the left part 10L of gearbox 10).Be fixed with driving gear 30 near the left side of transmission shaft 27 (internal surface of the wall portion of the left part 10L of gearbox 10), driving gear 30,31 engagements.Thus, with respect to the connecting part 10b of gearbox 10 (right side and left part 10R, 10L), the major part of input shaft 22 and transmission shaft 27 and driving gear 30,31 are configured in left side (the left part 10L of gearbox 10).

As Fig. 7 and shown in Figure 9, in the right side of transmission shaft 27 (the right side part 10R of gearbox 10), on transmission shaft 29, be embedded with the right side and left output gear 32R, 32L outside the rotation freely relatively, in the right side and the left side of right and left output gear 32R, 32L, right and left engaging piece 33R, 33L are by the rotation of spline structure one and outer sliding freely be embedded on the transmission shaft 29 (right engaging piece 33R is configured near the internal surface of wall portion of right side part 10R of gearbox 10).Between right output gear 32R and right engaging piece 33R, constitute right side clutch 34, between left output gear 32L and left engaging piece 33L, constitute left side clutch 34.

As shown in Figure 7, from the right and left support 10c of gearbox 10 (right side and left part 10R, 10L), to the right side and Left Drive case 14, be supported with transmission shaft 35, inside at gearbox 10 (right side and left part 10R, 10L), be fixed on driving gear 36 and right and left output gear 32R, 32L engagement on the transmission shaft 35, on the right side and the inside of Left Drive case 14, driving gear 37 is fixed on the transmission shaft 35.From the right side and Left Drive case 14 to right and left axle box 15, be supported with the right side and left axletree 38, on the right side and the inside of Left Drive case 14, be fixed on driving gear 39 and driving gear 37 engagements on the right side and the left axletree 38.In the inside of right and left axle box 15, right and left axletree 38 reaches the left side to the right and extends, and the sprocket wheel 1a of right and left crawler travel device 1 (with reference to Fig. 2 and Fig. 4) links with the right side of right and left axletree 38 and the end in left side.

According to above-mentioned structure, as shown in Figure 7, the power of input shaft 22 is via transmission shaft 27, driving gear 30,31, transmission shaft 29, the right side and left side clutch 34 (right and left engaging piece 33R, 33L), right and left output gear 32R, 32L, driving gear 36, transmission shaft 35, driving gear 37,39, the right side and left axletree 38, be passed to the right side and left crawler travel device 1, body directly advances.

[3]

The right side and left side clutch 34 hydraulic mechanism of usefulness (be equivalent to turn) then are described.

As shown in Figure 9, on the outer surface of the right side of transmission shaft 29 and left side, be formed with spline part 29a, but right and left engaging piece 33R, the rotation of 33L one and outer slidably freely being embedded on the spline part 29a of transmission shaft 29 are embedded on the spline part 29a of transmission shaft 29 but bearing part 40 one are outer rotatably.

As Fig. 9 and shown in Figure 10, the a plurality of recesses of configuration on the part of bearing part 40 sides of right and left engaging piece 33R, 33L, going up separately of the recess of right and left engaging piece 33R, 33L, dispose spring 41 doubly in inboard and the outside, by bearing part 40 and spring 41, the engagement side that right and left engaging piece 33R, 33L reach left output gear 32R, 32L to the right is subjected to the application of force.By engagement right and left engaging piece 33R, 33L and right and left output gear 32R, 32L, become the drive state of the right side and left side clutch 34, the power of transmission shaft 29 is passed to the right side and left crawler travel device 1 via the right side and left side clutch 34.

As shown in Figure 9, piston 42 can be configured between the right side and left output gear 32R, 32L and the transmission shaft 29 freely slidably, piston 42 and right and left engaging piece 33R, 33L butt, stride across the right side and left engaging piece 33R, 33L and piston 42 and be inserted with spring pin 43, so that piston 42 rotates integratedly with right and left engaging piece 33R, 33L.

As shown in Figure 9, if reach to the right and supply with action oil between left output gear 32R, 32L and the piston 42, then the right side and left engaging piece 33R, 33L and piston 42 overcome spring 41 and are extremely left a side from right and left output gear 32R, 32L by slide, become the dissengaged positions of the right side and left side clutch 34.If discharge the action oil between right and left output gear 32R, 32L and the piston 42, then the right side and left engaging piece 33R, 33L and piston 42 by the engagement side of slide to right and left output gear 32R, 32L, become the drive state of the right side and left side clutch 34 under the effect of spring 41.

In this case, as shown in Figure 9, by the right side and left engaging piece 33R, 33L and piston 42 splits ground are constituted, even right and left engaging piece 33R, 33L tilt for transmission shaft 29, piston 42 can not be subjected to yet the right side and left engaging piece 33R, 33L inclination influence and carry out slide.

As shown in Figure 9, right and left engaging piece 33R, 33L and piston 42, transmission shaft 29 constitute rotation integratedly and not relative mutually rotation by spring pin 43, produce speed discrepancy between the peripheral part of the interior perimembranous of the right side and left output gear 32R, 32L and piston 42.The part place that joins with the inner peripheral surface of right and left output gear 32R, 32L in the peripheral part of piston 42 is formed with a plurality of circle-shaped slot part 42a, make the part of action oil be maintained among the slot part 42a of piston 42, the scorification between the peripheral part that prevents piston 42 and the interior perimembranous of the right side and left output gear 32R, 32L.

As shown in Figure 9, in transmission shaft 29, middle body between the spline part 29a of the right side and left side constitutes the same diameter of no ladder difference, the turning clutch box 47 of aftermentioned [4], right and left output gear 32R, 32L, piston 42, right and left engaging piece 33R, 33L, accepts parts 40 and can assembling be installed from the right side of transmission shaft 29 and any one party of left side.

[4]

The structure of the transmission system (turning system) in the gearbox 10 (right side and left part 10R, 10L) then is described.

As Fig. 7 and shown in Figure 9, be supported with transmission shaft 44 across gearbox 10 (right side and left part 10R, 10L), relatively near the driving gear 45 of the outer freely right side (internal surface of the wall portion of the right side part 10R of gearbox 10) that is embedded in transmission shaft 44 of rotation meshes with the gear part of the peripheral part of right engaging piece 33R, possesses to shallow turn clutch (grand turn clutch) 46 hydraulic mechanism of usefulness (be equivalent to turn) between transmission shaft 44 and driving gear 45.Shallowing turn clutch 46, to be constituted as friction multi-plate, is operating as drive state by supplying with working oil, is operating as dissengaged positions by discharging working oil.

As Fig. 7 and shown in Figure 9, rotation is outer freely relatively is embedded on the transmission shaft 29 for turning clutch box 47, is fixed on the driving gear 47a engagement of the peripheral part of driving gear 48 on the transmission shaft 44 and turning clutch box 47.Turning clutch box 47 is constituted as bilateral symmetry, constitutes the right side and left-hand bend clutch 49 hydraulic mechanism of usefulness (be equivalent to turn) between turning clutch box 47 and right and left output gear 32R, 32L.It is multi-plate that the right side and left-hand bend clutch 49 are constituted as friction, is operating as drive state by supplying with working oil.In this case, in the right side and left-hand bend clutch 49, friction plate is closely configuration mutually, even working oil is discharged from, the right side and left-hand bend clutch 49 also become half drive state.

As Fig. 9 and shown in Figure 11, in turning clutch box 47, under the situation of accepting parts 54 of the ring-type that the friction plate of accepting the right side and left-hand bend clutch 49 is installed, possesses protuberance 54a on the parts 54 accepting, the protuberance 54a that accepts parts 54 enters into one of the opening portion 47b that protuberance entered of the friction plate of the right side of turning clutch box 47 and left-hand bend clutch 49, accepts parts 54 by spline.

Thus, as Fig. 7 and shown in Figure 9, shallow turn clutch 46 when being operating as drive state, the power of transmission shaft 29 via right engaging piece 33R, driving gear 45, shallow turn clutch 46, transmission shaft 44 and driving gear 48, as identical with transmission shaft 29 sense of rotation and, be passed to turning clutch box 47 than the power of transmission shaft 29 low speed.The right side or left side clutch 34 are being operating as dissengaged positions, when the right side or left-hand bend clutch 49 are operating as drive state, as identical with transmission shaft 29 sense of rotation and be passed to the right side or left output gear 32R, 32L than the power of transmission shaft 29 low speed.

As Fig. 7 and shown in Figure 9, possesses break 50 hydraulic mechanism of usefulness (be equivalent to turn) near the left side of transmission shaft 44 (outer surface of the wall portion of the left part 10L of gearbox 10).It is multi-plate that break 50 is constituted as friction, is operating as braking state by supplying with working oil, is operating as relieving state by discharging working oil.

Thus, as Fig. 7 and shown in Figure 9, when break 50 was operating as braking state, via transmission shaft 44 and driving gear 48, turning clutch box 47 became braking state.The right side or left side clutch 34 are operating as dissengaged positions, and on the right side or left-hand bend clutch 49 when being operating as drive state, right or left output gear 32R, 32L become braking state.

As Fig. 7 and shown in Figure 9, be fixed with driving gear 51 near the left side of transmission shaft 27 (internal surface of the wall portion of the left part 10L of gearbox 10), be embedded with driving gear 52 outside the rotation freely relatively near the left side of transmission shaft 44 (internal surface of the wall portion of the left part 10L of gearbox 10), driving gear 51,52 engagement possesses reversing clutch 53 hydraulic mechanism of usefulness (be equivalent to turn) between transmission shaft 44 and driving gear 52.It is multi-plate that reversing clutch 53 is constituted as friction, is operating as drive state by supplying with working oil, is operating as dissengaged positions by discharging working oil.

Thus, as Fig. 7 and shown in Figure 9, when reversing clutch 53 is operating as drive state, the power of transmission shaft 27 is via driving gear 51,52, reversing clutch 53, transmission shaft 44 and driving gear 48, as with the power of transmission shaft 29 rightabout rotations, be passed to turning clutch box 47.The right side or left side clutch 34 are operating as dissengaged positions, on the right side or left-hand bend clutch 49 when being operating as drive state, are passed to the right side or left output gear 32R, 32L with the power of transmission shaft 29 rightabout rotations.

As Fig. 7 and shown in Figure 9, the transmission of power that reversing clutch 53 will be opposite with side's direction of right or left crawler travel device 1 is transmitted bigger moment of torsion (reciprocal power) to the opposing party of right or left crawler travel device 1.Shallow turn the transmission of power of the low speed that clutch 46 will be identical with side's direction of right or left crawler travel device 1 the opposing party, transmit smaller moment of torsion (power of equidirectional low speed) to right or left crawler travel device 1.

Thus, reversing clutch 53 needs bigger diameter and a plurality of friction plate, and reversing clutch is than relatively large, and particularly external diameter is big.Shallowing turn clutch 46 can be that a smaller diameter and a minority friction plate gets final product, and it is more small-sized to shallow turn clutch 46, and particularly external diameter is little.

[5]

The operation of hydrostatic formula stepless speed changes devices 11 then is described.

As shown in figure 13, the pump of hydrostatic formula stepless speed changes devices 11 (being equivalent to the hydraulic type pump) 11P constitute to neutral position N, from neutral position N advance F high-speed side and retreat the high-speed side stepless change freely of R, the motor of hydrostatic formula stepless speed changes devices 11 (being equivalent to hydraulic motor) 11M constitutes height two-stage ground speed change freely.Possess the hydrostatic formula stepless speed changes devices 11 of operation pump 11P swash plate oil hydraulic cylinder 59, give the control valve 60 of row's operation element oil to oil hydraulic cylinder 59, the main shift lever (example of main transformer speed operation piece) 61 that is provided in Drive Section 5 mechanically is connected with control valve 60.Thus, by operation main shift lever 61, control valve 60 is operated, oil hydraulic cylinder 59 actions, and the swash plate of the pump 11P of hydrostatic formula stepless speed changes devices 11 is operated to the position corresponding to the operating position of main shift lever 61.

As shown in figure 13, possess the hydrostatic formula stepless speed changes devices 11 of operation motor 11M swash plate oil hydraulic cylinder 62, give the control valve 63 of the solenoid operated of row's operation element oil to oil hydraulic cylinder 62, possess varying speed switch 61a on the grip part of main shift lever 61, the operation signal of the varying speed switch 61a of main shift lever 61 is input in the control gear 64.Thus, by the varying speed switch 61a of operation main shift lever 61,64 operations of control valve 63 controlled devices, oil hydraulic cylinder 62 actions, the swash plate of the motor 11M of hydrostatic formula stepless speed changes devices 11 is operated at a high speed and low-speed position.

As shown in figure 13, the operating position sensor 65 that possesses the operating position that detects main shift lever 61, possess the gait of march sensor 79 of the gait of march that detects body, the checkout value of operating position sensor 65 and gait of march sensor 79 is input in the control gear 64.The swash plate of the motor 11M of hydrostatic formula stepless speed changes devices 11 in high speed position still at the detection of low-speed position operation signal, by control gear 64 identifications by the varying speed switch 61a of main shift lever 61.Thus, utilize the pump 11P of hydrostatic formula stepless speed changes devices 11 and the operating position of motor 11M, the gait of march of body, can discern Fig. 7 and secondary speed-changing device (shift component 28) shown in Figure 8 is in high speed position or at low-speed position.

In hydrostatic formula stepless speed changes devices 11 shown in Figure 13 and secondary speed-changing device (shift component 28), good drive state of mechanical efficiency and the bad drive state of mechanical efficiency are arranged.

Hydrostatic formula stepless speed changes devices 11 (pump 11P and motor 11M) under the high-speed region and secondary speed-changing device (shift component 28) high speed position, hydrostatic formula stepless speed changes devices 11 (pump 11P and motor 11M) under the low-speed region and secondary speed-changing device (shift component 28) at high speed position, hydrostatic formula stepless speed changes devices 11 (pump 11P and motor 11M) under low-speed region and in the state of secondary speed-changing device (shift component 28) at low-speed position, become the good drive state of mechanical efficiency.At hydrostatic formula stepless speed changes devices 11 (pump 11P and motor 11M) under high-speed region and under the state of secondary speed-changing device (shift component 28) at low-speed position, become the bad drive state of mechanical efficiency.

In this case, utilize the operation signal of varying speed switch 61a of checkout value, the main shift lever 61 of operating position sensor 65 and gait of march sensor 79, if in control gear 64 the hydrostatic formula stepless speed changes devices 11 of identification (pump 11P and motor 11M) under high-speed region and secondary speed-changing device (shift component 28) at the state of low-speed position, then in the operation panel (not shown) of Drive Section 5, demonstrate the bad drive state of mechanical efficiency, cause driver's attention.

Turning mode switch 78 of record in [8] described later [9] [10] [11], shallow turn state, wheel one stops one changes in pivot turn state and the wheel one positive one anti-pivot turn state, can select the state of shallowing turn, wheel one to stop one by turning mode switch 78 changes pivot turn state and wheel one positive one anti-pivot turn state, is to utilize the varying speed switch 61a of main shift lever 61 swash plate of the motor 11M of hydrostatic formula stepless speed changes devices 11 to be operated the state of low-speed position.If utilize the varying speed switch 61a of main shift lever 61, the swash plate of the motor 11M of hydrostatic formula stepless speed changes devices 11 is operated the state of high speed position, then irrelevant with the operating position of turning mode switch 78, be chosen as the state of shallowing turn.

In addition, in following explanation, so-called " shallowing turn (grand turn) ", be moving device 1 about instigating to equidirectional (direction of advance), and with different speed driving mutually, thereby make the body turning with bigger radius of turn.So-called " wheel one stops one and changes pivot turn (pivotturn) " is that a side moving device 1 drives and stops about instigating, and the opposing party's moving device 1 driven, thereby body is turned.So-called " wheel one positive one anti-pivot turn (spin turn) ", be that moving device 1 about instigating is to a different direction (direction direction of advance mutually, the other direction direction of retreat), and with mutual different speed driving, thereby body is turned than " wheel one stops one and changes pivot turn " little radius of turn.

[6]

Then, the hydraulic unit 57 that reaches left side clutch 34 (right and left engaging piece 33R, 33L), the right side and left-hand bend clutch 49 to the right, shallows turn clutch 46, break 50, reversing clutch 53 row's of giving operation element oil is described.

As Fig. 3 and shown in Figure 8, in the input shaft 11b of hydrostatic formula stepless speed changes devices 11, with the part (the right horizontal sidepiece of hydrostatic formula stepless speed changes devices 11) of input shaft 16 opposition sides on be connected with supply pump 55 and oil hydraulic pump 56, the input shaft 11b that constitutes by hydrostatic formula stepless speed changes devices 11 drives supply pump 55 and oil hydraulic pump 56, and the working oil of supply pump 55 is supplied to hydrostatic formula stepless speed changes devices 11.

As Fig. 3 and shown in Figure 7, hydraulic unit 57 links with the outer surface of the horizontal sidepiece of left supporting frame 2 sides of gearbox 10 (left part 10L), is connected with hydraulic unit 57 from the outside pipe arrangement 58 (with reference to Figure 12) of oil hydraulic pump 56.Shown in the solid line of Fig. 2, Fig. 3, Fig. 4, be lowered by under the state of driving at reaping part 4 (supporting frame 2), supporting frame 2 is positioned at the left lateral outer side of hydraulic unit 57.Shown in the double dot dash line of Fig. 4, be urged under the state of the upper limit by being risen at reaping part 4 (supporting frame 2), supporting frame 2 is positioned at the top of the left lateral outer side of hydraulic unit 57.

Shown in Fig. 1,2,3,4, is risen to be urged at reaping part 4 (supporting frame 2) and prescribed a time limit, reaping part 4 forwards leaves the top from the front portion of body, therefore in the left side of the front portion of body, open between the front portion of reaping part 4 and body, the worker can enter between the front portion of reaping part 4 and body from the left side of the front portion of body.

In this case, shown in Fig. 1,2,3,4, hydraulic unit 57 links with the outer surface of the horizontal sidepiece of left supporting frame 2 sides of gearbox 10 (left part 10L), therefore the worker is when the left side of the front portion of body enters between the front portion of reaping part 4 and body, for the worker, hydraulic unit 57 is positioned at a side nearby (operator side) of gearbox 10, and the upkeep operation of hydraulic unit 57 carries out easily.

[7]

Then, illustrate hydraulic unit 57 structure (right side and left side clutch 34 (right and left engaging piece 33R, 33L), the right side and left-hand bend clutch 49, shallow turn the oil hydraulic circuit structure of clutch 46, break 50, reversing clutch 53).

Shown in Fig. 5,7,9, transmission shaft 29,44 is supported in the gearbox 10 (right side and left part 10R, 10L) along left and right directions, the left part of transmission shaft 29,44 connects the wall portion of the left part 10L of gearbox 10, and is inserted into the inside of hydraulic unit 57.From the left part of transmission shaft 29, to the right side and left side clutch 34 (right and left engaging piece 33R, 33L), the right side and left-hand bend clutch 49, possesses oil circuit 29b in the inside of transmission shaft 29.From the left part of transmission shaft 44, to shallowing turn clutch 46 and reversing clutch 53, possesses oil circuit 44a in the inside of transmission shaft 44.In the inside of hydraulic unit 57, possesses break 50 in the end of transmission shaft 44.

As shown in figure 12, in the inside of hydraulic unit 57, possess right-hand bend control valve 67 (being equivalent to control valve), left-hand bend control valve 68 (being equivalent to control valve), safety valve 69 (being equivalent to control valve), feather valve 70 (being equivalent to control valve), proportional control valve 71 (being equivalent to control valve), turning switching control valve 72 (being equivalent to control valve), guide operating valve 73,74 (being equivalent to control valve).Outside pipe arrangement 58 from oil hydraulic pump 56 is connected with hydraulic unit 57, be formed with a plurality of oil circuits (not shown) on the link surface (junction plane) of the outer surface of hydraulic unit 57 and gearbox 10 (left part 10L), the right side and left-hand bend control valve 67,68, safety valve 69, feather valve 70 are connected on the oil circuit 66 that is connected with outside pipe arrangement 58 side by side via the oil circuit of link surface (junction plane).Be formed with the discharge oil circuit on the link surface (junction plane) of the outer surface of hydraulic unit 57 and gearbox 10 (left part 10L), the working oil of safety valve 69 and feather valve 70 is back to gearbox 10 (right side and left part 10R, 10L) via above-mentioned discharge oil circuit.

As shown in figure 12, right-hand bend control valve 67 is connected with right side clutch 34 (right engaging piece 33R) and right-hand bend clutch 49 via the oil circuit of link surface (junction plane) and the oil circuit 29b of transmission shaft 29.Left-hand bend control valve 68 is connected with left side clutch 34 (left engaging piece 33L) and left-hand bend clutch 49 via the oil circuit of link surface (junction plane) and the oil circuit 29b of transmission shaft 29.

As shown in figure 12, the right side and left-hand bend control valve 67,68 constitute can operate the solenoid operated of supplying with position 67a, 68a and drain position 67b, 68b freely, is subjected to the application of force to drain position 67b, 68b.Feather valve 70 constitutes the solenoid operated that can operate off-position 70a and drain position 70b freely, and 70a is subjected to the application of force to off-position.From the oil circuit 75 of branch between the oil circuit 29b of the right side and left-hand bend control valve 67,68 and transmission shaft 29, be connected in series proportional control valve 71 and turning switching control valve 72, turning switching control valve 72 is via the oil circuit of link surface (junction plane) and the oil circuit 44a of transmission shaft 44, with shallow turn clutch 46 and be connected with reversing clutch 53, turning switching control valve 72 is connected with break 50 via the oil circuit 76 of hydraulic unit 57.

As shown in Figure 9, from the oil circuit 44b of the oil circuit 44a branch of transmission shaft 44 be connected transmission shaft 29 and shallow turn between the clutch 46, and transmission shaft 29 and reversing clutch 53 between, the part of working oil that constitutes the oil circuit 44a of transmission shaft 44 supply to transmission shaft 29 and shallow turn between the clutch 46, and transmission shaft 29 and reversing clutch 53 between, shallow turn with reversing clutch 46,53 and be cooled.

As shown in Figure 9, shallow turn and reversing clutch 46,53 piston 46a, be formed with recess 46b on the 53a with the ring-type of transmission shaft 29 concentric circles, 53b, if working oil is supplied to and shallows turn and reversing clutch 46,53, shallow turn and reversing clutch 46,53 piston 46a, 53a moves (the piston 46a of for example shallowing turn clutch 46 moves to the paper left of Fig. 9), shallow turn and reversing clutch 46,53 are operating as drive state, and then driving gear 45,54 friction plate support enters shallows turn and reversing clutch 46,53 piston 46a, the recess 46b of 53a, among the 53b.Thus, transmission shaft 29 and shallow turn between the clutch 46, and transmission shaft 29 and reversing clutch 53 between close by shallowing turn with piston 46a, the 53a of reversing clutch 46,53, the working oil of cooling usefulness be difficult to from transmission shaft 29 and shallow turn between the clutch 46, and transmission shaft 29 and reversing clutch 53 between spill.

As shown in figure 12, proportional control valve 71 constitutes solenoid operated, can carry out the flow control of working oil.Turning switching control valve 72 constitutes to operate freely and shallows turn position 72a, wheel one and stop a pilot operated formula of changeing pivot turn position 72b and wheel one positive one anti-pivot turn position 72c, is subjected to the application of force to shallowing turn position 72a.Constitute guide operating valve 73, operate wheel one so that will be supplied to turning switching control valve 72 and stop a commentaries on classics pivot turn position 72b from guide's working oil of oil circuit 75 branches, constitute guide operating valve 74, so that will be supplied to turning switching control valve 72 from guide's working oil of oil circuit 75 branches and operate wheel one positive one anti-pivot turn position 72c.

[8] [9] [10] [11] are described as described later is operated by control gear 64 for the right side and left-hand bend control valve 67,68, feather valve 70, proportional control valve 71, guide operating valve 73,74.

[8]

Then explanation utilizes the straight moving condition of deflecting bar 77.

As shown in figure 13, in Drive Section 5, be equipped with and reach left side operation deflecting bar 77 freely to the right, the operating position of deflecting bar 77 is input in the control gear 64, and deflecting bar 77 constitutes can be operated straight carry freely and put N, the right side and a left side the 1st turning position R1, L1, right side and left the 2nd turning position R2, L2.Be equipped with turning mode switch 78 in Drive Section 5, the operating position of turning mode switch 78 is input in the control gear 64, and turning mode switch 78 possesses the position of shallowing turn, wheel one stops one changes pivot turn position and wheel one positive one anti-pivot turn position.

As Figure 12 and shown in Figure 13, irrelevant with the operating position of turning mode switch 78, if deflecting bar 77 is operated into straight carry and puts N, then the right side and left-hand bend control valve 67,68 are operated into drain position 67b, 68b, feather valve 70 is operated into drain position 70b, working oil from the right side and left side clutch 34 (right and left engaging piece 33R, 33L), the right side and left-hand bend clutch 49 discharge, the right side and left side clutch 34 (right and left engaging piece 33R, 33L) are operating as drive state, and the right side and left-hand bend clutch 49 are operating as half drive state.Shallow turn with reversing clutch 46,53 and be operating as dissengaged positions by proportional control valve 71, break 50 is operating as relieving state.

Thus, as described in Fig. 7 and above-mentioned [2] [4], the power of input shaft 22 is via transmission shaft 27, driving gear 30,31, transmission shaft 29, the right side and left side clutch 34 (right and left engaging piece 33R, 33L), right and left output gear 32R, 32L, driving gear 36, transmission shaft 35, driving gear 37,39, the right side and left axletree 38, be passed to the right side and left crawler travel device 1, body directly advances.

[9]

Then explanation utilizes the state of shallowing turn of deflecting bar 77.

As Figure 12 and shown in Figure 13, as if being operated, turning mode switch 78 shallows turn the position, and the switching control valve of then turning 72 is operated into by guide operating valve 73,74 and shallows turn position 72a.Thus, if deflecting bar 77 is operated into right the 1st turning position R1, the control valve 67 of then turning right is operated into supplies with position 67a, feather valve 70 is operated into off-position 70a, working oil is supplied to right side clutch 34 (right engaging piece 33R) and right-hand bend clutch 49, right side clutch 34 (right engaging piece 33R) is operating as dissengaged positions, and right-hand bend clutch 49 is operating as drive state.

In this case, as Fig. 7 and shown in Figure 9, left-hand bend clutch 49 is half drive state, therefore the power of left side clutch 34 (left engaging piece 33L) is passed to right output gear 32R from left output gear 32L and left-hand bend clutch 49 via right-hand bend clutch 49, identical with transmission shaft 29 sense of rotation and than transmission shaft 29 slightly the power of low speed be passed to right output gear 32R.Thus, body changes direction at leisure to the right.

As Figure 12 and shown in Figure 13, if deflecting bar 77 is operated right the 1st turning position R1, the control valve 67 of then turning right as mentioned above is operated into and supplies with position 67a, feather valve 70 is operated into off-position 70a, simultaneously, working oil begins via proportional control valve 71 and turning switching control valve 72 (shallowing turn position 72a) and is supplied to shallow turn clutch 46, from right the 1st turning position R1 the 2nd turning position R2 operation to the right, the working pressure of shallowing turn clutch 46 is more by proportional control valve 71 boost operations more for deflecting bar 77.

As Fig. 7 and shown in Figure 9, operating position based on deflecting bar 77, the working pressure of shallowing turn clutch 46 is by proportional control valve 71 boosted operations, accompany with it, the power of transmission shaft 29 via right engaging piece 33R, driving gear 45, shallow turn clutch 46, transmission shaft 44, driving gear 48, turning clutch box 47 and right-hand bend clutch 49, will be identical with transmission shaft 29 sense of rotation and than the transmission of power of transmission shaft 29 low speed to right output gear 32R.

In this case, as Fig. 7 and shown in Figure 9, become from the power of left side clutch 34 (left engaging piece 33L) and be passed to the state of right output gear 32R from the power of shallowing turn clutch 46 simultaneously, therefore in the working pressure of shallowing turn clutch 46 is the scope of low pressure, power from left side clutch 34 (left engaging piece 33L) surpasses from the power of shallowing turn clutch 46, and right output gear 32R is used to be driven from the power of left side clutch 34 (left engaging piece 33L).Thus, in the working pressure of shallowing turn clutch 46 was the scope of low pressure, body changed direction at leisure to the right.

Then, if shallowing turn the working pressure of clutch 46 near right the 2nd turning position R2, the operating position of deflecting bar 77 becomes high pressure, then as Fig. 7 and shown in Figure 9, better than the power from left side clutch 34 (left engaging piece 33L), right output gear 32R is used to be driven from the power of shallowing turn clutch 46 from the power of shallowing turn clutch 46.Under this state, the driving that is subjected to compared with right output gear 32R from the power of left side clutch 34 (left engaging piece 33L), right output gear 32R is subjected to the bigger driving from the power of shallowing turn clutch 46, and right output gear 32R is driven with low speed, and body is shallowed turn to the right.

As Figure 12 and shown in Figure 13, if deflecting bar 77 is operated a left side the 1st turning position L1, the control valve 68 that then turns left is operated into supplies with position 68a, feather valve 70 is operated into off-position 70a, working oil is supplied to left side clutch 34 (left engaging piece 33L) and left-hand bend clutch 49, left side clutch 34 (left engaging piece 33L) is operating as dissengaged positions, and left-hand bend clutch 49 is operating as drive state.Meanwhile, carry out operation same as described above, body changes direction at leisure left.If deflecting bar 77 is operated a left side the 2nd turning position L2 from a left side the 1st turning position L1, then carry out operation same as described above, body is shallowed turn left.

[10]

Then explanation utilizes the wheel one of deflecting bar 77 to stop one changes the pivot turn state.

As Figure 12 and shown in Figure 13, if being operated wheel one, turning mode switch 78 stops a commentaries on classics pivot turn position, the switching control valve of then turning 72 is operated into wheel one and stops a commentaries on classics pivot turn position 72b by guide operating valve 73,74.Thus, if deflecting bar 77 is operated into right the 1st turning position R1, the control valve 67 of then turning right is operated into supplies with position 67a, feather valve 70 is operated into off-position 70a, working oil is supplied to right side clutch 34 (right engaging piece 33R) and right-hand bend clutch 49, right side clutch 34 (right engaging piece 33R) is operating as dissengaged positions, and right-hand bend clutch 49 is operating as drive state.In this case, left-hand bend clutch 49 is half drive states, so body and above-mentioned [9] similarly change direction at leisure to the right.

As Figure 12 and shown in Figure 13, if deflecting bar 77 is operated right the 1st turning position R1, then as mentioned above, right-hand bend control valve 67 is operated into supply position 67a and feather valve 70 is operated into off-position 70a, simultaneously, working oil begins to be supplied to break 50 via proportional control valve 71 and turning switching control valve 72 (wheel one stops and changes pivot turn position 72b), from right the 1st turning position R1 the 2nd turning position R2 operation to the right, the working pressure of break 50 is more by proportional control valve 71 boost operations more for deflecting bar 77.

As Fig. 7 and shown in Figure 9, operating position based on deflecting bar 77, the working pressure of break 50 accompanies with it by proportional control valve 71 boosted operations, and braking force arrives right output gear 32R via transmission shaft 44, driving gear 48, turning clutch box 47 and right-hand bend clutch 49.

In this case, as Fig. 7 and shown in Figure 9, become the state that is passed to right output gear 32R from the braking force of the power of left side clutch 34 (left engaging piece 33L) and break 50 simultaneously, therefore the working pressure at break 50 is in the scope of low pressure, surpass the braking force of break 50 from the power of left side clutch 34 (left engaging piece 33L), right output gear 32R is used to be driven from the power of left side clutch 34 (left engaging piece 33L).Thus, be in the scope of low pressure in the working pressure of break 50, body changes direction at leisure to the right.

Then, if the operating position of deflecting bar 77 is near right the 2nd turning position R2, the working pressure of break 50 becomes high pressure, then as Fig. 7 and shown in Figure 9, the braking force of break 50 surpasses the power from left side clutch 34 (left engaging piece 33L), right output gear 32R utilizes the braking force of break 50 to become braking state, and body wheel one to the right stops a commentaries on classics pivot turn.

As Figure 12 and shown in Figure 13, if deflecting bar 77 is operated a left side the 1st turning position L1, the control valve 68 that then turns left is operated into supplies with position 68a, feather valve 70 is operated into off-position 70a, working oil is supplied to left side clutch 34 (left engaging piece 33L) and left-hand bend clutch 49, left side clutch 34 (left engaging piece 33L) is operating as dissengaged positions, and left-hand bend clutch 49 is operating as drive state.Meanwhile, carry out operation same as described above, body changes direction at leisure left.If deflecting bar 77 is operated a left side the 2nd turning position L2 from a left side the 1st turning position L1, then carry out operation same as described above, body stops one to left wheel one and changes pivot turn.

As Figure 12 and shown in Figure 13, on the grip part of deflecting bar 77, has reversing switch 77a.As described in above-mentioned [9], be operated at turning mode switch 78 and shallow turn the position, shallow turn the state from the right side or the left side of right (left side) the 1st turning position R1 (L1) (left side) the 2nd turning position R2 (L2) operation to the right deflecting bar 77, produce needs with littler semidiameter turn.

In this case, as Figure 12 and shown in Figure 13, with deflecting bar 77 under the state of right (left side) the 1st turning position R1 (L1) (left side) the 2nd turning position R2 (L2) operation to the right, if the reversing switch 77a of pressing operation deflecting bar 77, the switching controls of then turning is read 72 and is operated into wheel one and stops one and change pivot turn position 72b from shallowing turn position 72a, and body (left side) wheel one to the right stops one and changes pivot turn.Only during the reversing switch 77a of pressing operation deflecting bar 77,, this wheel one changes the pivot turn state for stopping one, if hand is taken away operation from the reversing switch 77a of deflecting bar 77, the switching control valve of then turning 72 stops one from wheel one changes pivot turn position 72b and is operating as and shallows turn position 72a, and body returns the state of shallowing turn.

[11]

Then explanation utilizes the wheel one positive one anti-pivot turn state of deflecting bar 77.

As Figure 12 and shown in Figure 13, if turning mode switch 78 is operated wheel one positive one anti-pivot turn position, the switching control valve of then turning 72 is operated into wheel one positive one anti-pivot turn position 72c by guide operating valve 73,74.Thus, if deflecting bar 77 is operated right the 1st turning position R1, the control valve 67 of then turning right is operated into supplies with position 67a, feather valve 70 is operated into off-position 70a, working oil is supplied to right side clutch 34 (right engaging piece 33R) and right-hand bend clutch 49, right side clutch 34 (right engaging piece 33R) is operating as dissengaged positions, and right-hand bend clutch 49 is operating as drive state.In this case, left-hand bend clutch 49 is half drive states, so body and above-mentioned [9] similarly change direction at leisure to the right.

As Figure 12 and shown in Figure 13, if deflecting bar 77 is operated right the 1st turning position R1, then as mentioned above, right-hand bend control valve 67 is operated into supply position 67a and feather valve 70 is operated into off-position 70a, simultaneously, working oil begins to be supplied to reversing clutch 53 via proportional control valve 71 and turning switching control valve 72 (wheel one positive one anti-pivot turn position 72c), from right the 1st turning position R1 the 2nd turning position R2 operation to the right, the working pressure of reversing clutch 53 is more by proportional control valve 71 boosted operations more for deflecting bar 77.

As Fig. 7 and shown in Figure 9, operating position based on deflecting bar 77, the working pressure of reversing clutch 53 is by proportional control valve 71 boosted operations, accompany with it, the power of transmission shaft 27 is via driving gear 51,52, reversing clutch 53, transmission shaft 44, driving gear 48, turning clutch box 47 and right-hand bend clutch 49, as being passed to right output gear 32R with the power of transmission shaft 29 direction of rotation.

In this case, as Fig. 7 and shown in Figure 9, become from the power of left side clutch 34 (left engaging piece 33L) and be passed to the state of right output gear 32R from the power of reversing clutch 53 simultaneously, therefore the working pressure at reversing clutch 53 is in the scope of low pressure, surpass power from reversing clutch 53 from the power of left side clutch 34 (left engaging piece 33L), right output gear 32R is by the motivational drive from left side clutch 34 (left engaging piece 33L).Thus, be in the scope of low pressure in the working pressure of reversing clutch 53, body changes direction at leisure to the right.

Then, at approaching right the 2nd turning position R2 of the operating position of deflecting bar 77, when the working pressure of reversing clutch 53 becomes high pressure, as Fig. 7 and shown in Figure 9, surpass power from left side clutch 34 (left engaging piece 33L) from the power of reversing clutch 53, right output gear 32R is by the motivational drive from reversing clutch 53.Under this state, right output gear 32R is driven to opposite direction with respect to left output gear 32L, body wheel one positive one anti-pivot turn to the right.

As Figure 12 and shown in Figure 13, if deflecting bar 77 is operated a left side the 1st turning position L1, the control valve 68 that then turns left is operated into supplies with position 68a, feather valve 70 is operated into off-position 70a, working oil is supplied to left side clutch 34 (left engaging piece 33L) and left-hand bend clutch 49, left side clutch 34 (left engaging piece 33L) is operating as dissengaged positions, and left-hand bend clutch 49 is operating as drive state.Meanwhile, carry out operation same as described above, body changes direction at leisure left.If deflecting bar 77 is operated a left side the 2nd turning position L2 from a left side the 1st turning position L1, then carry out operation same as described above, body changes pivot turn to left wheel one positive.

[12]

Shown in Fig. 8 and Figure 17～18, the hydrostatic formula stepless speed changes devices of putting as the main transformer quick-mounting (HST) but 11 pump 11P that in HST case 11A, possess the axial plunger type of stepless transformation rotational speed, can be with the motor 11M of rotational speed speed change for the axial plunger type of height two-stage, link these pumps 11P and motor 11M with closed-loop path 81, and constitute hydrostatic formula stepless speed changes devices 11.

Pump 11P is used for coming the movable swash plate 11D of the convertible rotational speed of drive controlling to constitute by a plurality of bi-directional drive cylinders 82, is used for controlling the working oil that is dropped into bi-directional drive cylinder 82 by solenoid-operated proportional control valve 83 and constitutes.

On the other hand, motor 11M is used for coming drive controlling that the movable swash plate 11D of convertible rotational speed is constituted by a plurality of bi-directional drive cylinders 84, is used for being made of by the working oil of input bi-directional drive cylinder 84 85 controls of two electromagnetic type connection-cut-off valves.

Like this, motor 11M constitutes volume-variable.And the pressure cylinder capacity of the employed pressure cylinder Capacity Ratio of motor 11M pump 11P is big, and pressure cylinder is configured to and the control angle of movable swash plate 11D can be set at two-stage.

With respect to the bi-directional drive cylinder 84 of motor 11M, the force application spring 86 that returns the application of force to low-speed position is set, in a side motion space so that under the situation that solenoid valve 85 breaks down, divide a word with a hyphen at the end of a line to low speed side.

Like this, in bi-directional drive cylinder 84, owing to only make force application spring 86 generation effects in side's side of piston 87, thus the movement speed difference of piston 87, but can realize the adjustment of movement speed throttle orifice 88 being set to giving in the oil extraction road of bi-directional drive cylinder 84.

According to above structure, operation advance and the road on the switching of advancing undertaken by motor 11M being switched to height.

As Figure 14～shown in Figure 16, in the Drive Section 5,6 the next door in the driver's seat, the main shift lever 61 of stepless change ground operating pumps 11P is set to and can operates freely front and back, and the grip part 61A of main shift lever 61 is provided with the switch 61a of motor 11M speed change for the height two-stage.

And, at the body that stops to advance, cut off main switch after, connect under the situation of main switch again, motor 11M is irrelevant with the state that cuts off main switch, and is set to lower-speed state.

As Fig. 8 and shown in Figure 180, be decided to be input shaft 11b with accepting input shaft from the transmission of power of motor 7 as the pump shaft of pump 11P, input shaft 11b is provided with from HST case 11A is outstanding, on the outstanding input shaft 11b that is provided with doubly-linked ground be equipped with to closed-loop path 81 supply with the supply pump 55 of working oil and the hydraulic coupling that in gearbox (transmission), is adopted etc. supply with working oil as the gearbox oil hydraulic pump 56 of pump.Separate supply pump 55 and oil hydraulic pump 56 with Sealing, use the working oil of dividing other system as working oil.

Structure in the gearbox 10 then is described.As shown in Figures 7 and 8, set up the input shaft 22 of acceptance, set up transmission shaft 27 abreast as secondary variable-speed shaft with input shaft 22 from the transmission of power of hydrostatic formula stepless speed changes devices 11 at an end of gearbox 10.Between input shaft 22 and transmission shaft 27, be provided with can height two-stage speed change the secondary gear A of gear type, be provided with the B of stopping brake mechanism at an end of transmission shaft 27.

The secondary gear A of gear type is described.As Fig. 7 and shown in Figure 19, the pine commentaries on classics is supported with two gears 25,26 of size on input shaft 22 and transmission shaft 27, disposes clutch sleeve 28 between two gears 25,26 of size, makes the gear part 27a engagement of clutch sleeve 28 and transmission shaft 27.

By optionally making clutch sleeve 28 and a side of big small gear 25,26 and the gear part 27a engagement of transmission shaft 27, formation can present the secondary gear A of gear type of high lower-speed state.

Clutch sleeve 28 all is set to fast state when advancing when operation is advanced and on the road, is switched to low speed side only to use under the situation when promptly escaping etc.

Like this, the secondary gear A of gear type when common advancing not by variable speed operation, the range fork 150 of operated clutch sleeve 28 is installed on the service axis 151 sliding freely, the camshaft 152 that drives this range fork 150 that slides is bearing on the gearbox 10, on the end that the ratio gearbox 10 of camshaft 152 is given prominence to, is connected with the operating arm 128A of secondary speed change lever (example of secondary variable speed operation spare) 128 usefulness.As Figure 11 and Figure 14～shown in Figure 15, the secondary speed change lever 128 that is connected on the operating arm 128A uprightly is provided with from the side of gearbox 10, is being configured under the state of the outer surface of Drive Section 5.That is, carry out in secondary speed change lever 128 configurations that the switching of the secondary gear A of gear type regulates outside the riding manipulation space.

Structure in the gearbox 10 is described.As shown in Figure 7, set up the transmission shaft (running shaft) 44 that is useful on the rotation speed change abreast with transmission shaft 27 and carried the transmission shaft (side clutch shaft) 29 of side clutch 34,34 etc., be provided with driving gear of exporting to transmission shaft 44 51 and the driving gear of exporting to transmission shaft 29 30 at the secondary gear A of the gear type of transmission shaft 27 with between stopping with arrestment mechanism B.

In gearbox, can shallow turn beyond directly advancing, zig zag, wheel one stops one changes 3 kinds of turning actions of pivot turn, on the axle in above-mentioned transmission shaft 44 and transmission shaft 29, transmission downstream side each clutch and the gear that can carry out these turning actions is set.

Pine changes the driving gear 52 be supported with above-mentioned driving gear 51 engagements on transmission shaft 44, and is adjacent with driving gear 52 and be equipped with and stop one as the multi-plate wheel one of friction and change the reversing clutch 53 of pivot turn with clutch.

As shown in Figure 9, the clutch boss 53A that reversing clutch 53 comprises and driving gear 52 is integrally formed, be fixed on clutch main body 53B on the transmission shaft 44, be installed in many plates of friction 53C, piston 53a between them.The multi-plate break C that advances of friction of zig zag usefulness is installed at an end of transmission shaft 44.Be provided with across the other end of reversing clutch 53 and the break C opposition side of advancing and shallow turn clutch 46, change being supported with driving gear 45 another distolateral pine of shallowing turn clutch 46.

As shown in Figure 9, on transmission shaft 29, install with turning power to the left and right either party's crawler travel device 1 carry out the multi-plate turning clutch 49 of friction of transmission of power, in order to accept transmission of power from reversing clutch 53 that is fixed on transmission shaft 44 and the driving gear 48 of shallowing turn between the clutch 46, turning clutch 49 is equipped with the driving gear 47a with driving gear 48 engagements.

As Fig. 7, Fig. 9 and shown in Figure 17, be that driving gear 45 pine of shallowing turn the clutch boss of clutch 46 changes and is bearing on the transmission shaft 44 with double as, and with spline be fastened on the transmission shaft 29 about a side gear 33 engagements of side clutch 34.By such structure, return transmission shaft 44 in case will shallow turn power from transmission shaft 29, will be passed to driving gear 48 and turning clutch 49.Left and right sides the opposing party's side clutch 34 is set on the opposing party of transmission shaft 29, and constituting can be to axletree 38 output.

In the side side of left and right sides the opposing party's side clutch 34, pine changes and is supported with driving gear 31, with driving gear 30 engagements that are arranged on the transmission shaft 27, is used to accept the transmission of power from transmission shaft 27.

The linkage structure of right side clutch 34 and turning clutch 49 is as described below.Between the clutch box 47B of the gear 33 of right side clutch 34 and turning clutch 49, pine changes and is supported with the right clutch sleeve 32 that breaks away from freely and be also used as the clutch boss of turning clutch 49 with gear 33 engagements.And this right clutch sleeve 32 has towards the 32R of output gear portion that axletree 38 is exported.

As shown in Figure 9, between right clutch sleeve 32 and gear 33, be folded with the piston 42 of hydraulic type, this piston 42 accept pressure oil and with gear 33 withstand effects, thereby be switched in engagement and be subjected to the state that the gear 33 of the application of force leaves from right clutch sleeve 32 on the direction, gear 33 and right clutch sleeve 32 reach the clutch dissengaged positions.If pressure relief oil, then pushed piston 42 and move it, with 32 engagements of right clutch sleeve by spring energized gear 33.

As shown in Figure 7, right clutch sleeve 32 constitutes with driving gear 36 engagements can carry out transmission of power to axletree 38, and described driving gear 36 is installed in as being arranged on the transmission shaft 35 of the pony axle between axletree 38 and the transmission shaft 29.

Then, as Fig. 7 and shown in Figure 9, the structure of left side clutch 34 is described.The structure of left side clutch 34 is different with the structure of right side clutch 34.That is, be not equivalent to the structure of gear 33, the clutch boss 45 that does not possess gear constitutes with left clutch sleeve 32 engagements that also belong to turning clutch 49 and breaks away from freely, constitutes left side clutch 34.Clutch boss 45 is subjected to the application of force by spring to the direction with 32 engagements of left clutch sleeve.

According to above-mentioned structure,, then will be passed to axletree 38 via left side clutch 34 as straight precession power from transmission shaft 27 directly via the rotating power of this driving gear 31 to transmission shaft 29 importings if left side clutch 34 is set at on-state.If left side clutch 34 is set at dissengaged positions, then can export turning power to axletree 38 by turning clutch 49 as described above.

According to above-mentioned structure, present 3 turn conditions.Drive path towards a side's (left side) who keeps gait of march crawler travel device 1 transmission when directly advancing in addition, is as described below.

Power from input shaft 22 transmits as follows: be installed in driving gear 30-spline on the transmission shaft 27 and be fastened on the left clutch sleeve 26-Left Drive gear 36-Left Drive axle 35-left side axletree 38 that driving gear 31-left side clutch (the side clutch under this situation is an on-state) 34-on the transmission shaft 29 is also used as turning clutch 49.

Drive path towards the opposing party's (right side) crawler travel device 1 transmission when shallowing turn is as described below.

Such as Fig. 7 and shown in Figure 9, transmit as follows from the power of input axle 22: be installed in turn the slowly clutch case 46A-power transmission shaft 44-of clutch 46 of travelling gear 45-that gear 33-that travelling gear 30-pine on the power transmission shaft 27 turns the travelling gear 31-right side clutch (the side clutch in this situation is the cut-out state) 34 that is bearing on the power transmission shaft 29 is also used as the clutch boss of the clutch 46 of turning slowly and be installed in travelling gear 48-on the power transmission shaft 44 and possess the right axletree 38 of the right power transmission shaft 35-of the right travelling gear 36-of right clutch sleeve 32-with the turning clutch 49-turning clutch 49 of the travelling gear 47a of travelling gear 48 engagements.

It is as described below that wheel one stops a drive path towards the opposing party's (right side) crawler travel device 1 transmission when changeing pivot turn.

In this case, a side's (left side) crawler travel device 1 is kept straight moving condition.That is, the power from input shaft 22 transmits as follows: the driving gear 30-pine that is installed on the transmission shaft 27 changes a clutch sleeve 26-left side the 5th input gear 22-Left Drive axle 35-left side axletree 38 that driving gear 31-left side clutch (the side clutch under this situation the is an on-state) 34-that is bearing on the transmission shaft 44 is also used as turning clutch 49.

The crawler travel device 1 on right side, becomes wheel one and stops one and change the pivot turn state to opposite (retreating) direction rotation with 1/3rd speed of the crawler travel device 1 in left side.Promptly, as Fig. 7 and shown in Figure 9, transmit as follows from the power of input shaft 22: being installed in driving gear 51-pine on the transmission shaft 27 changes the clutch main body 53B-transmission shaft 44-that is bearing in driving gear (the clutch boss of reversing clutch 53) the 52-reversing clutch 53 on the transmission shaft 44 and is installed in driving gear 48-on the transmission shaft 44 and possesses the right axletree 38 of the right transmission shaft 35-of right clutch sleeve 32-driving gear 36-with the turning clutch 49-turning clutch 49 of the driving gear 47a of driving gear 48 engagements.

Drive path towards the opposing party's (right side) crawler travel device 1 transmission when shallowing turn is as described below.

Wherein, in this case, a side's (left side) crawler travel device 1 is kept straight moving condition.That is, the power from input shaft 22 transmits as follows: the driving gear 30-pine that is installed on the transmission shaft 27 changes the left clutch sleeve 32-Left Drive gear 36-Left Drive axle 35-left side axletree 38 that driving gear 31-left side clutch (the side clutch under this situation the is an on-state) 34-that is bearing on the transmission shaft 44 is also used as turning clutch 49.

As Fig. 7 and shown in Figure 9, transmission shaft 44 is provided with the break C that advances, and utilizes hydraulic pressure that this break C that advances is switched to connection.By this break C that advances, braking force is transmitted as follows: be fixed on right side clutch connection-right clutch sleeve 32 (right side clutch 34 is cut off)-right axletree 38 of the right transmission shaft 35-of the right driving gear 36-of driving gear 36-that driving gear 48-on the transmission shaft 44 makes turning clutch 49.

Be set at fast state at the motor 11M with above-mentioned hydrostatic formula stepless speed changes devices 11, under the situation of the operation of turning, the turning pattern adopts the pattern of shallowing turn.Thus, when on the way advancing, zig zag pattern or wheel one do not occur and stop a commentaries on classics pivot turn pattern, guarantee the stability of advancing.

The structure of the B of stopping brake mechanism then is described.As Figure 19～shown in Figure 22, brake housing 133 is embedded on the 10A of installation base portion of the supporting drive shaft 27 that remains on gearbox 10, and in brake housing 133, take in wet friction multi-plate brake disks 134 and crimping and act on cam disk 135 on this brake disks 134, constitute the stopping brake B of mechanism.

From the backing 133A of the inboard of brake housing 133 to being provided with cam mechanism E with the back side of the opposed cam disk 135 of this backing 133A.As Figure 21 and shown in Figure 22, at three places of the circumferencial direction of backing 133A, embed and keep ball 136, and, form the card complex hole 135A that engages with above-mentioned ball 136 at three places of the circumferencial direction at the back side of cam disk 135.Card complex hole 135A be provided with towards the circumferencial direction one direction engaging degree of depth and engaging width shoal gradually and attenuate induce face 135a.

Constitute cam mechanism E by cam disk 135 and ball 136 here.

Backing 133A with card complex hole 135A diverse location and same radius position on, imbed fixed guide pin 137, the outstanding front end that guide finger 137 is set from the surface of backing 133A.Formation from the back side of cam disk 135 enter in the wall thickness and have to a certain degree the depth and along the engaging slotted hole 135B of circumferencial direction, constitute under the state of the both fixed positions that cam disk 135 are installed in brake housing 133, guide finger 137 is fastened in the engaging slotted hole 135B.

As Fig. 9 and Figure 19～shown in Figure 22, taking in mounting in engaging slotted hole 135B has helical spring 138, is taking in this helical spring 138 of mounting from the guide finger 137 that is inserted in the engaging slotted hole 135B under the state of the end of engaging slotted hole 135B.By this helical spring 138 and the resistance when cam disk 135 is rotated in a circumferential direction and to the Return-ing direction application of force.This helical spring 138 is called the return spring that cam disk 135 is rotated to Return-ing direction (opposite direction).

As shown in figure 21, be provided with through hole 135C, allow the entering of axle head of transmission shaft 27 in the rotating center position of cam disk 135.The cam disk 135 of packing in the inboard of brake housing 133, and the multi-plate brake disc of wet friction 134 is arranged in the inlet side mounting of cam disk 135.

As shown in figure 21, brake disc 134 more be provided with compression plate 139 near the ingress, compression plate 139 utilizes the hole with stopping wheel 140 and by anticreep.

According to above-mentioned structure, if carried out under the state of anticreep processing make the multi-plate brake disc 134 of cam disk 135, wet friction, compression plate 139 with stopping wheel 140 by the hole, be installed on the transmission shaft 27, then the axle head of transmission shaft 27 enters among the through hole 135C of cam disk 135.

Explanation is to the operating device of the B of stopping brake mechanism.Shown in Figure 19～22, on the outer surface of brake housing 133, be formed with the through hole 133B that is communicated with the accommodation space of taking in cam disk 135 grades, the boss part 133C that order possesses through hole 133B gives prominence to.With boss part 133C outstanding retainer 133D that is formed with tapped hole 133a that is provided with on the position of radially leaving fixed intervals.Be embedded in the service axis 141 that keeps connecting stopping brake operation piece (not shown) at the through hole 133B of boss part 133C, service axis 141 is constituted can be around the axis rotation of through hole 133B.On service axis 141, form the groove 141a that O type ring is used, O type ring 142 is installed, and give to circumferential rotational resistance, and to the moving resistance of axial direction.

As Figure 19～shown in Figure 22, make the shaft end 141b of service axis 141 more outstanding than boss part 133C, operating arm 143 is attached on the shaft end 141b.Between the top end 133c of the base end part 143A of operating arm 143 and boss part 133C, bolt stop is fixed with the rotation confinement plate 144 that operating arm 143 is rotated restriction.Rotation confinement plate 144 adopts following structure: be formed with the base end part 144A that is embedded in the inserting hole on the service axis 141 outside being used for, tip portion 144B extends towards the retainer 133D that is formed with tapped hole 133a from base end part 144A, hold up at tip portion 144B and to form the through hole 144C that bolt stop uses and the 144D of the stop limit portion of accepting of operating arm 142, make cam disk 135 be positioned at the break on positi.In addition, be positioned at the break on positi, force application spring (not shown) also can be set in order to make cam disk 135.

As Figure 19～shown in Figure 22,, be formed with the cam hole 135b in the recessed wall thickness at back side circumferencial direction one place of cam disk 135.Relative therewith, be fixed on service axis 141 on the operating arm 142 on the top end of cam disk 135, outstandingly being provided with eccentric projection 141c.By this off-centre projection 141c is engaged with the cam hole 135b of cam disk 135, and rotary manipulation operating arm 142, can be around transmission shaft 27 rotary manipulation cam disks 135.

For operating arm 143, though not shown, be provided with bindiny mechanism, can utilize the operation piece that is arranged on riding manipulation portion to operate.

According to above-mentioned structure, during operating operation spare, operating arm 143 is operated to the position of imaginary line b as shown in figure 20 from the position of solid line a.So, cam disk 135 is rotated operation, and from the break dissengaged positions shown in Figure 21 (a), shown in Figure 21 (b), cam disk 135 is pushed brake disc 134, presents the break on-state.

If cam disk 135 rotation, then the face 135a that induces at card complex hole 135A also climbs up under the state on the ball 136, and cam disk 135 is pushed brake disc 134 at leisure.Thus, can make break carry out ON Action.

[13]

The detailed structure of left and right sides moving device 1,1 then is described with reference to Figure 23～Figure 30.Moving device 1 possesses the identical structure in the left and right sides, so only illustrates the moving device 1 in left side in these accompanying drawings, and has omitted the diagram of the moving device 1 on right side.

Figure 23 is the side view of moving device 1.Figure 24 is the plan view of moving device 1.As shown in these figures, moving device 1 constitutes: possess the main orbit framework 210 along fore-and-aft direction, on this main orbit framework 210, possess the preceding swing track-frame 211 and the back swinging track framework 212 that support side by side at fore-and-aft direction, on preceding swing track-frame 211, possess what fore-and-aft direction supported side by side and four groundedly take turns 213 (below be called before ground engaging stabiliser wheel 213), on back swinging track framework 212, possess what fore-and-aft direction supported side by side and four groundedly take turns 214 (below be called rear ground engaging wheel 214), possesses crawler driving whell 215 than preceding ground engaging stabiliser wheel 213 and rear ground engaging wheel 214 side configuration forwards, the adjusting idler wheel 216 that disposes rearward than preceding ground engaging stabiliser wheel 213 and rear ground engaging wheel 214, the last upper saw pulley 217 of the top of the top of ground engaging stabiliser wheel 213 and rear ground engaging wheel 214 possesses along crawler driving whell 215 before being configured in, four preceding ground engaging stabiliser wheels 213, four rear ground engaging wheels 214, adjusting idler wheel 216, crawler belt 218 with two rubber systems that go up upper saw pulley 217 and reel.

Above-mentioned main orbit framework 210 is supported in the supporting frame portion 207 of advancing that is arranged on the organism frame 100 via the descending operation mechanism 240 of swing armite 241,242 a pair of before and after possessing.Advance supporting frame portion 207 by constituting via the sagittal tube material of body that is attached on the organism frame 100 by a pair of binding parts 208,208 in front and back.

Above-mentioned crawler driving whell 215 rotations are bearing on the gearbox 10 of the front end that is arranged on organism frame 100 freely.This crawler driving whell 215 utilizes the gearbox of advancing (not shown) of the inside that is positioned at gearbox 10 and is switched and drives to advance side and retreat side, to march forward side or retreat the mode driving track 218 of side rotation along preceding ground engaging stabiliser wheel 213, rear ground engaging wheel 214, adjusting idler wheel 216 and last upper saw pulley 217.Upper saw pulley 217 pine commentaries on classics are supported in the supporting frame portion 207 of advancing freely on each.

The linking department of setting up cylindrical shell in the centre of the length direction of preceding swing track-frame 211 and being provided with, and the front end of main orbit framework 210 set up cylindrical shell and be provided with support 210a utilize fulcrum 221 and relatively rotation link freely, preceding swing track-frame 211 with the horizontal axle center of the body of fulcrum 221 swing up and down as swinging center P1 by pivot suspension on support 210a.

Above-mentioned four preceding ground engaging stabiliser wheels 213 are positioned at the mode to the body rear side than swinging center P1 with the swinging center P1 that two preceding ground engaging stabiliser wheels 213 are positioned at than preceding swing track-frame 211 to body front side, two preceding ground engaging stabiliser wheels 213, decentralized configuration on fore-and-aft direction, and the pine commentaries on classics is supported on the preceding swing track-frame 211 freely.

The linking department of setting up cylindrical shell in the centre of the length direction of above-mentioned back swinging track framework 212 and being provided with, and the rearward end of above-mentioned main orbit framework 210 set up cylindrical shell and the support 210b that is provided with utilizes fulcrum 222 and relatively rotation link freely, back swinging track framework 212 with the horizontal axle center of the body of fulcrum 222 swing up and down as swinging center P2 by pivot suspension on support 210b.

Above-mentioned four rear ground engaging wheels 214 are positioned at the mode to the body rear side than swinging center P2 with the swinging center P2 that two rear ground engaging wheels 214 are positioned at than back swinging track framework 212 to body front side, two rear ground engaging wheels 214, decentralized configuration on fore-and-aft direction, and the pine commentaries on classics is supported on the back swinging track framework 212 freely.

Above-mentioned adjusting idler wheel 216 with through rear ground engaging wheel 214 or the crawler belt 218 of going up upper saw pulley 217 forwards the mode returned of side the inner surface side of crawler belt 218 is carried out leading role.This adjusting idler wheel 216 is supported on the rearward end of back swinging track framework 212 via the supporting structure H of the supporting mass 225 with square tube shape, and adjusting idler wheel 216 pines change the rearward end that is attached at described supporting mass 225 freely.

Swing track-frame 211 and back swinging track framework 212 possess crawler belt guider 219 before above-mentioned.The crawler belt guider 219 of each track-frame 211,212 is fastened between the axle projection of pairing left and right of crawler belt 218, prevents that ground engaging stabiliser wheel 213,214 breaks away from from crawler belt 218.

Figure 25 is the vertical profile side view of above-mentioned supporting structure H.Figure 26 is the plan view of above-mentioned supporting structure H.As shown in these figures, above-mentioned supporting structure H, except possessing above-mentioned supporting mass 225, also possess the rearward end of back swinging track framework 212 set up the sheet metal parts and the maintenance tube 226 of the square tube shape that is provided with, be arranged on the inside of this maintenances tube 226 tension spring 227, reach tension adjustment thread spindle 228.

Above-mentioned maintenance tube 226 makes the forward end of supporting mass 225 embedded sliding freely and it is kept.

Above-mentioned tension spring 227 is clipped at the spring of the inside that keeps tube 226 and accepts body 229 and be arranged between the spring abutting part 225a on the supporting mass 225.That is, tension spring 227 is pushed as the counter-force parts and is acted on that spring abutting part 225a goes up and to from keeping the outstanding sides of tube 226 to the supporting mass 225 slip application of forces, thus to adjusting idler wheel 216 butt application of force on crawler belt 218 by spring being accepted body 229.

Above-mentioned spring is accepted body 229 and is retained as slip freely in the inside that keeps tube 226, and combines with tension adjustment thread spindle 228 screw threads.Mobile Regulation spring is accepted body 229 along keeping tube 226 by rotary manipulation for tension adjustment thread spindle 228, increases and decreases adjusting idler wheel 216 that adjusting produces by the tension spring 227 withstand effect power towards crawler belt 218 thus.

As shown in figure 23, swing track-frame 211 and back swinging track framework 212 configuration as follows before above-mentioned: the body center of gravity G of working machine under the state of working machine at horizontal plane by preceding swing track-frame 211 and after on the vertical straight line between the swinging track framework 212.

That is, at working machine when the bigger eminence of ladder difference moves to lower, while the generation that the ground connection can suppress the integral body of moving device 1 and be reduced to lower the time is impacted makes it move.

That is, Figure 27 (a) (b) be make working machine from eminence S to the advance side view of the moving device 1 when mobile of lower T.

Shown in Figure 27 (a), along with advancing of working machine is mobile, body center of gravity G is moved to the lower side from eminence S, and the forward end of moving device 1 drops to lower T and ground connection, and moving device 1 becomes from eminence S to lower T the state with the attitude ground connection of tilting to the front lower place.So, the preceding track-frame 211 of swinging is swung around swinging center P1 owing to the ground connection counter-force of the forward end that acts on moving device 1, the rear end side of preceding swing track-frame 211 descends with respect to main orbit framework 210, and the preceding ground engaging stabiliser wheel 213 before being supported on the swing track-frame 211 is ground connection on lower T or slope C easily.

Shown in Figure 27 (b), when working machine is moved further, back swinging track framework 212 is by the ground connection counter-force of the rear end side that acts on moving device 1 and swing around swinging center P2, the forward end of back swinging track framework 212 descends with respect to main orbit framework 210, and the rear ground engaging wheel 214 after being supported on the swinging track framework 212 is ground connection on lower T or slope C easily.Since these, on one side moving device 1 make a plurality of before ground engaging stabiliser wheels 213 and rear ground engaging wheel 214 in early days ground connection drop to lower T, the generation of the ground connection impact the when integral body that suppresses moving device 1 drops to lower T.

Working machine is being retreated under the mobile situation from high to lower, when moving device 1 becomes lateral attitude from lower T to eminence S ground connection, back swinging track framework 212 is positioned at downside, preceding swing track-frame 211 is positioned at upside, and is different with the mobile situation of advancing on the relative position this point on the above-below direction with back swinging track framework 212 at preceding swing track-frame 211.But, identical with the mobile situation of advancing on ground connection this point on lower T or the slope C easily by the ground engaging stabiliser wheel 213,214 of back swinging track framework 212 and preceding swing track-frame 211 supportings.

If preceding swing track-frame 211 and back swinging track framework 212 are swung, then utilize preceding ground engaging stabiliser wheel 213 that the swing by preceding swing track-frame 211 causes with respect to the rear ground engaging wheel 214 that moves and cause by the swing of back swinging track framework 212 of main orbit framework 210 with respect to the moving of main orbit framework 210, can produce the steering force of the direction that the tension force that makes crawler belt 218 increases.At this moment, adjusting idler wheel 216 is with 212 swings of back swinging track framework, and the direction that relaxes towards the tensioning that makes crawler belt 218 moves.And, even the tension force of crawler belt 218 increases, along with this tension force increases, tension spring 227 resiliently deformables, adjusting idler wheel 216 is to keeping tube 226 sides to return mobile.The tension force that suppresses crawler belt 218 thus increases.

As shown in figure 23, the moving device 1 swing limting mechanism 230 that possesses intermediate portion, be provided with to preceding swing track-frame 211 and back swinging track framework 212 from main orbit framework 210.

Figure 28 is the side view of swing limting mechanism 230.Figure 29 is the plan view of swing limting mechanism 230.As shown in these figures, swing limting mechanism 230 possesses the extended preceding limitation part 233 of swinging limiting rod 231, swinging the extension end of limiting rod 232 from the extended back swing of the front end of back swinging track framework 212 limiting rod 232, the extension end that rotates swing limiting rod 231 before supporting freely and back of rearward end of swinging track framework 211 in the past.

Preceding swing limiting rod 231 is swung with respect to preceding swing track-frame 211 around the axle center of the connection pin 234 that links this connecting rod 231 and preceding swing track-frame 211.The back is swung limiting rod 232 and is swung with respect to back swinging track framework 212 around the axle center of the connection pin 35 that links this connecting rod 232 and back swinging track framework 212.Limitation part 233 is arranged on the main orbit framework 210.This limitation part 233 slidably reach rotation enter freely be arranged on before swing limiting rod 231 the extension end slotted hole 236 and be arranged in the slotted hole 237 of extension end of back swing limiting rod 232.

Along with the angle of oscillation of preceding swing track-frame 211 with respect to main orbit framework 210 increases, swing track-frame 211 before limitation part 233 stretches via preceding swing limiting rod 231 and supports, swing track-frame 211 is in the swing boundary before making.Along with the angle of oscillation of back swinging track framework 212 with respect to main orbit framework 210 increases, limitation part 233 makes back swinging track framework 212 be in the swing boundary via back swing limiting rod 232 stretching supporting back swinging track frameworks 212.Thus, the swing of swing track-frame 211 and back swinging track framework 212 before the restriction of swing limting mechanism 230, even make preceding swing track- frame 211 and 212 swings of back swinging track framework, what crawler belt 218 did not take place yet crosses pine or tension.

As shown in figure 30, the forward end of preceding swing track-frame 211 is made as U with respect to main orbit framework 210 from the full swing angle of the preceding swing track-frame 211 of neutral position uplifted side, the forward end of preceding swing track-frame 211 is made as D with respect to main orbit framework 210 from the full swing angle of the preceding swing track-frame 211 of neutral position decline side.The angle of oscillation of swing track-frame 211 before 230 restrictions of swing limting mechanism, the above-mentioned full swing angle U of swing track-frame 211 is littler than above-mentioned full swing angle D before making.

As Figure 23 and shown in Figure 24, above-mentioned descending operation mechanism 240 constitutes except possessing a pair of swing armite 241 in above-mentioned front and back, 242, also possess the binding connecting rod 243 of the rearward end of the swing armite 242 that links rear side and main orbit framework 210, freely the swing armite 241 of front side is attached at the preceding operating arm 245 that the one rotation is provided with freely on the rotation fulcrum 244 in the supporting frame portion 207 of advancing in rotation, freely the swing armite 242 of above-mentioned rear side is attached at the back operating arm 247 that the one rotation is provided with freely on the rotation fulcrum 246 in the above-mentioned supporting frame portion 207 of advancing in rotation, make the continuous motion stem 248 of above-mentioned preceding operating arm 245 and above-mentioned back operating arm 247 interlocks, the oil hydraulic cylinder 249 that links from above-mentioned back operating arm 247 to pressure cylinder carriage 249a that organism frame 7 possessed.

Descending operation mechanism 240 comes operating arm 247 after the swinging operation by oil hydraulic cylinder 249, thereby rotary manipulation rotation fulcrum 246, the swing armite 242 of swinging operation rear side is swung armite 242 by this up and down, the rear end side of descending operation main orbit framework 210 via linking connecting rod 243.And, by above-mentioned back operating arm 247, via continuous motion stem 248, operating arm 245 before the swinging operation, by this preceding operating arm 245 rotary manipulations rotation fulcrum 244, the swing armite 241 of swinging operation front side up and down, by the forward end of these swing armite 241 descending operation main orbit frameworks 210, thus with moving device 1 with respect to organism frame 100 descending operation abreast.

Promptly, respectively by this descending operation mechanism 240 with the moving device 1 in left side, by this descending operation mechanism 240 with the moving device 1 on right side with respect to organism frame 100 descending operations, and the lifting travel by the moving device about making 1 is identical, and makes changing highly abreast over the ground of organism frame 100.

Respectively by this descending operation mechanism 240 with the moving device 1 in left side, by this descending operation mechanism 240 with the moving device 1 on right side with respect to organism frame 100 descending operations, and lifting travel difference by the moving device about making 1, the body of advancing tilts at left and right directions with respect to ground, the variable height over the ground about organism frame 100.That is, the body of advancing tilts to the left and right with respect to ground.

As mentioned above, above-mentioned crawler travel device 1 have on the fore-and-aft direction side by side a plurality of ground engaging stabiliser wheels 213,214, than above-mentioned a plurality of ground engaging stabiliser wheels be positioned at the body front side crawler driving whell 215, be positioned at the adjusting idler wheel 216 of body rear side and the crawler belt 218 of being reeled than above-mentioned a plurality of ground engaging stabiliser wheels along above-mentioned crawler driving whell, above-mentioned a plurality of ground engaging stabiliser wheels, above-mentioned adjusting idler wheel.

In such crawler travel device in the past, a plurality of ground engaging stabiliser wheels are belonged to the status packet of ground connection wheels with two ground engaging stabiliser wheels, possess two ground engaging stabiliser wheels with each ground connection wheels and be attached at cantilever on the track-frame.Each cantilever swingingly is being supported on the track-frame up and down freely via fulcrum shaft.Each cantilever makes two ground engaging stabiliser wheels disperse than the distolateral forward and rear end side of fulcrum shaft and it is supported (for example, opening 2001-260956 communique (JP-A-2001-260956) with reference to the spy of Japan, particularly paragraph [0012] [0015], Fig. 1-4).

In crawler travel device,, consider to use above-mentioned conventional art for the generation of vibration that the ladder difference that can suppress by the ground of advancing causes.But, use under the situation of above-mentioned conventional art, following problem is also arranged.

For example combine-harvester will enter the field, garden from furrow sometimes.Advance when mobile to lower from the bigger eminence of such ladder difference, along with the body center of gravity moves to the lower side from eminence, the forward end of moving device descends and ground connection to lower, becomes moving device and strides across lower and the eminence state with the attitude ground connection that has a down dip forward.At this moment, become because of moving device is a lateral attitude state that causes ground engaging stabiliser wheel more between lower and eminence to float from ground.After this, the rear end side of moving device is left from eminence if move continuation, then becomes the state of the integral body of moving device lower ground connection.Like this, ground connection is reduced to lower and during the ground connection up to rear end side reducing to lower from the forward end of moving device, keeps the number of the ground engaging stabiliser wheel of the state that floats from ground to become many.Its result, the ground connection when moving device integral body drops to lower is impacted and is become big easily.

Retreat under the situation about moving from high to lower, to lower ground connection, moving device strides across lower and eminence and the lateral attitude of ground connection becomes the attitude that has a down dip backward, also exists and the identical problem of mobile situation of advancing from rear end side for moving device.

With respect to this, being characterized as of above-mentioned crawler travel device 1 has following structure.That is,

This crawler travel device 1 possess side by side a plurality of ground engaging stabiliser wheels 213,214 of fore-and-aft direction, than above-mentioned a plurality of ground engaging stabiliser wheels be positioned at the body front side crawler driving whell 215, be positioned at the adjusting idler wheel 216 of body rear side and the crawler belt 218 of being reeled than above-mentioned a plurality of ground engaging stabiliser wheels, wherein along above-mentioned crawler driving whell and above-mentioned a plurality of ground engaging stabiliser wheel and above-mentioned adjusting idler wheel

Possess the main orbit framework 210 that is supported on the organism frame 100, the preceding swing track-frame 211 and the back swinging track framework 212 that on above-mentioned main orbit framework, on fore-and-aft direction, are supported abreast and swing freely up and down around the horizontal swinging center of body respectively

A part that makes above-mentioned a plurality of ground engaging stabiliser wheel 213,214 on preceding swing track-frame 211, disperse to be bearing in swinging center than swing track-frame 211 before this to the body front side with to the body rear side,

The remaining part that makes above-mentioned a plurality of ground engaging stabiliser wheel 213,214 on back swinging track framework 212, disperse to be bearing in swinging center than this back swinging track framework 212 to the body front side with to the body rear side,

Above-mentioned adjusting idler wheel 216 is bearing on the back swinging track framework 212.

According to this structure, under the mobile situation of advancing from high to lower, the forward end of crawler travel device 1 descends and ground connection to lower, if crawler travel device 1 becomes lower and the eminence state with the attitude ground connection tilted to the front lower place that strides across, swing track-frame 211 is by the ground connection counter-force of the forward end that acts on crawler travel device 1 then, with respect to 210 swings of main orbit framework, before the rear end side of swing track-frame 211 descend with respect to organism frame 100, by the ground engaging stabiliser wheel 213 of preceding swing track-frame 211 supportings ground connection on lower or slope easily.And, continue if move, then back swinging track framework 212 is by the ground connection counter-force of the rear end side that acts on crawler travel device 1, with respect to 210 swings of main orbit framework, the forward end of back swinging track framework 212 descends with respect to organism frame 100, by the ground engaging stabiliser wheel 214 of back swinging track framework 212 supportings ground connection on lower or slope easily.

On the other hand, retreat from high to lower under the mobile situation, when crawler travel device 1 becomes the lateral attitude that strides across lower and eminence ground connection, back swinging track framework 212 is positioned at downside, preceding swing track-frame 211 is positioned at upside, different with the mobile situation of advancing on the relative position this point on the above-below direction at preceding swing track-frame 211 with back swinging track framework 212, but, at ground engaging stabiliser wheel 213 by back swinging track framework 212 and 211 supportings of preceding swing track-frame, 214 is identical with the mobile situation of advancing on ground connection this point on lower or the slope easily.

If preceding swing track- frame 211 or 212 swings of back swinging track framework, then utilize with the ground engaging stabiliser wheel 213,214 of preceding swing track-frame 211 or back swinging track framework 212 swings with respect to the moving of main orbit framework 210, produce the steering force that the tension force that makes crawler belt 218 increases sometimes.If 212 swings of back swinging track framework, then adjusting idler wheel 216 is with 212 swings of back swinging track framework, and the direction that relaxes towards the tensioning that makes crawler belt 218 moves, and the tension force that suppresses crawler belt 218 increases.

Thus, when the big eminence of ladder difference moves to the lower, in any one situation about moving that moves forward and backward, can make a plurality of ground engaging stabiliser wheels 213,214 lower or slope ground connection, and descend when the tension force that suppresses crawler belt 218 increases and move, the ground connection the when integral body that is difficult to produce crawler travel device 1 drops to lower is impacted, and aspect such as sensation is good taking, and be difficult for producing deterioration, can access working machine good aspect durability because of the tensioning of crawler belt 218.

And in above-mentioned crawler travel device 1, above-mentioned main orbit framework 210 descending operations are supported on the organism frame freely.

According to this structure, make main orbit framework 210 with respect to organism frame 100 liftings, can change organism frame 100 to ground level.Thus, even if soft ground and crawler belt 218 avales earthward, also can with organism frame 100 ground level is adjusted to high value, can prevent that the earth of body from adhering to etc., and advantageously carry out operation.

And, in above-mentioned crawler travel device 1, possess the rearward end swing of in the past swinging track framework 211 extended freely before swing limiting rod 231, before the extended freely back swing of the front end swing limiting rod 232 of back swinging track framework 212, the rotation supporting freely the extension end of the extension end of swing limiting rod 231 and back swing limiting rod 232 so that the limitation part 233 of the swing restriction of swing track-frame 211 and back swinging track framework 212 before carrying out.

According to this structure, along with preceding swing track-frame 211 increases with respect to the angle of oscillation of main orbit framework 210, by limitation part 233 supporting that is stretched, preceding swing track-frame 211 is in the swing boundary to preceding swing track-frame 211 via preceding swing limiting rod 231.Along with the angle of oscillation of back swinging track framework 212 with respect to main orbit framework 210 increases, back swinging track framework 212 is swung limiting rod 232 by limitation part 233 supporting that is stretched via the back, and back swinging track framework 212 is in the swing boundary.

Thus, not excessive in order to swing track-frame 211 before limiting with the swing of back swinging track framework 212, can utilize the limting mechanism simple in structure (swing limting mechanism 230) of same limitation part 233 supportings to realize by swing limiting rod 231 before making and back swing limiting rod 232, can obtain simple in structurely preventing that the excessive swing because of preceding swing track-frame 211 and back swinging track framework 212 from producing the structure of crossing problems such as pine or tension of crawler belt 218.

And, in above-mentioned crawler travel device 1, possess the tension spring 227 of above-mentioned adjusting idler wheel 216 withstand effects on crawler belt 218.

According to this structure, even because the mobile tension force of crawler belt 218 that makes of the ground engaging stabiliser wheel that the swing of preceding swing track-frame 211 or back swinging track framework 212 causes increases, along with this tension force increases, tension spring 227 resiliently deformables, adjusting idler wheel 216 is return mobile, and the tension force that can suppress crawler belt 218 increases.

Thus, not only can swing, can also return mobile by the one of adjusting idler wheel 216 and back swinging track framework 212 by adjusting idler wheel 216, suppress to be increased with respect to the tension force of the mobile crawler belt that causes 218 of main orbit framework 210 by ground engaging stabiliser wheel, the durability that can improve crawler belt 218 makes the deterioration that more difficult generation is caused by the tension of crawler belt 218.

And in above-mentioned crawler travel device 1, in side view, body center of gravity G is on by the vertical straight line between preceding swing track-frame 211 and the back swinging track framework 212.

According to this structure, advance to move and retreat in moving any one in utilization and carry out under from high to lower the situation about moving, can both when impacting, ground connection carry out being difficult for producing.

Promptly, from high to lower mobile utilization is advanced move the situation of carrying out and utilize to retreat and move under the situation of carrying out, G is moved to the lower side from eminence by the body center of gravity, the forward end of moving device 1 or rear end side descend and ground connection to lower, and moving device 1 strides across lower and eminence becomes state with heeling condition ground connection.Because body center of gravity G is by preceding swing track-frame 211 with afterwards on the vertical straight line between the swinging track framework 212, from high to lower mobile utilization is advanced move under the situation of carrying out, along with moving device 1 strides across the state of the attitude ground connection that lower and eminence have a down dip before being switching to, preceding swing track-frame 211 is in early days with respect to organism frame 100 swings.

On the other hand, mobile utilization is from high to lower retreated under the mobile situation of carrying out, along with moving device 1 strides across the state of the attitude ground connection that has a down dip after lower and eminence are switching to, back swinging track framework 212 is in early days with respect to organism frame 100 swings.

Thus, under the mobile situation of advancing and retreat under the mobile situation, the ground engaging stabiliser wheel 213,214 that all makes swing track-frame 211 before utilizing or back swinging track framework 212 supportings is in early days lower or slope ground connection, descends in the generation of can the ground connection when suppressing to drop to lower impacting.

[other mode of executions]

(1) in the structure of Fig. 3 and Fig. 7, the right side of gearbox 10 and the first from left side's sidepiece and the opposing party's sidepiece can be configured about as described below on the contrary and constitute.

In this case, be formed with the recess 10a of ladder difference shape in the outside on the top of the left part 10L of gearbox 10, in plan view, recess 10a enters near (slightly to the paper right side) of the connecting part 10b of gearbox 10 (right side and left part 10R, 10L).Hydrostatic formula stepless speed changes devices 11 is configured in the mode of the recess 10a that enters gearbox 10 (left part 10L), the oral area block 11a of hydrostatic formula stepless speed changes devices 11 is attached on the recess 10a of gearbox 10 (left part 10L), and the input shaft 11b of hydrostatic formula stepless speed changes devices 11 and input shaft 12, support unit 12 extend to the right.

In the top of gearbox 10 (right side and left part 10R, 10L), input shaft 22 is fixed with driving gear 30,31 to be supported in the gearbox 10 (right side part 10R) in abutting connection with the mode of (opposed) with the recess 10a of gearbox 10 (left part 10L) near the right side of transmission shaft 27,29 (internal surface of the wall portion of the right side part 10R of gearbox 10).In the left side of transmission shaft 29 (gearbox 10 left part 10L), right and left output gear 32R, 32L can rotate freely outer being embedded on the transmission shaft 29 relatively, and right and left engaging piece 33R, 33L are by the rotation of spline structure one and outer sliding freely be embedded on the transmission shaft 29 (left engaging piece 33L is configured near the internal surface of wall portion of gearbox 10 left part 10L).Shallow turn clutch 46 and be provided in the right side of transmission shaft 44, reversing clutch 53 is provided in the left side of transmission shaft 44.

(2) in the above-described embodiment, gearbox 10 (right side and left part 10R, 10L) and hydrostatic formula stepless speed changes devices 11 are constituted by split, but also gearbox 10 (right side and left part 10R, 10L) and hydrostatic formula stepless speed changes devices 11 can be constituted integratedly with a casing.

Can be not yet with the output shaft 11c of hydrostatic formula stepless speed changes devices 11 with input shaft 22 splits constitute and utilize a transmission shaft (not shown) to constitute.The power that also can constitute the output shaft 11c of hydrostatic formula stepless speed changes devices 11 is passed to input shaft 22 via driving gear (not shown).

As the stepless speed changes devices (the main transformer quick-mounting is put) of the usefulness of advancing, might not be limited to the such hydrostatic formula stepless speed changes devices 8 of diagram.Also can use the stepless speed changes devices of belt for example or with the stepless speed changes devices of hydrostatic formula stepless speed changes devices and planetary pinion combination.

(3) in Fig. 7, can discard break 50, make reversing clutch 53 possess the function of break 50 and constitute.

In this case, described in above-mentioned [11], be passed to simultaneously under the state of a left side (right side) output gear 32L (32R) from the power of right (left side) side clutch 34 (right (left side) engaging piece 33R (33L)) with from the power of reversing clutch 53, set the working pressure of reversing clutch 53, become the state of balance so that make, make a left side (right side) output gear 32L (32R) become the state that stops from the power of right (left side) side clutch 34 (right (left side) engaging piece 33R (33L)) with from the power of reversing clutch 53.

(4) in Fig. 2, can constitute Drive Section 5 is provided in the left lateral outer side of gearbox 10, supporting frame 2 is provided in the right lateral outer side of gearbox 10.If such structure then links the outer surface of hydraulic unit 57 with the horizontal sidepiece of right supporting frame 2 sides of gearbox 10 (right side part 10R).

Also can constitute, hydraulic unit 57 is not provided in the outer surface of the horizontal sidepiece of gearbox 10 (right side and left part 10R, 10L), and be provided in right or left horizontal sidepiece in the inside of gearbox 10 (right side and left part 10R, 10L), the switch cap freely of the maintenance usefulness of hydraulic unit 57 is provided in the outer surface of the horizontal sidepiece of gearbox 10 (right side and left part 10R, 10L).

(5) shift component 28 of secondary speed-changing device (gear type secondary gear A) can be constituted by oil hydraulic cylinder (not shown) and carry out slide (hydraulic mechanism that the speed change that is equivalent to advance is used), perhaps also can utilize a plurality of hydraulic couplinges to constitute secondary speed-changing devices (hydraulic mechanism that the speed change that is equivalent to advance is used).

Utilize a plurality of hydraulic couplinges to constitute under the situation of secondary speed-changing device, hydraulic coupling is bearing on the transmission shaft 27, the right side of transmission shaft 27 or left part are inserted in the hydraulic unit 57, possess oil circuit up to hydraulic coupling in the inside of transmission shaft 27 from the right side or the left part of transmission shaft 27.

(6) the hydraulic motor 8C that constitutes hydrostatic formula stepless speed changes devices 8 can adopt movable swash plate 8D is fixed as certain angle of inclination, only carries out capacity regulating by hydraulic type pump 6B and carries out the structure of speed change.Perhaps on the contrary, also can in hydraulic motor 8C, make movable swash plate 8D infinitely regulate.

(7) can adopt the method that drives the movable swash plate 8D of hydraulic type pump 6B by electric actuator such as electric motors, and adopt by sensor such as potentiometers to go out actuating quantity, based on the structure of this checkout value control electric actuator as the main shift lever 61 of main transformer speed operation piece.

(8) use bi-directional drive cylinder 8d to come drive controlling hydraulic type pump 8B, for movement speed being made as necessarily, throttle orifice 8h is set on feed path, but also can be provided with especially.

Claims (9)

1. the drive mechanism of advancing of an operating vehicle, with the power of motor via the stepless speed changes devices of the usefulness of advancing and gearbox and be passed to the right side and left lateral motion device,

Form to the right at right or left side's sidepiece place of above-mentioned gearbox or recess that the opposing party's side on a left side enters, with right or left the opposing party's sidepiece of the gearbox of above-mentioned recess adjacency in be equipped with input shaft,

At the advance stepless speed changes devices of usefulness of the recess place of above-mentioned gearbox configuration, the output shaft of the stepless speed changes devices of the above-mentioned usefulness of advancing is provided in the recess side of above-mentioned gearbox and links with the input shaft interlock,

The driving gear that side is downstream transmitted the power of above-mentioned input shaft is provided in the input shaft sidepiece of above-mentioned gearbox,

To the opposing party's sidepiece and the power of supporting drive shaft, above-mentioned driving gear is passed to the input shaft sidepiece of this transmission shaft, be equipped with the right side and left side clutch from right or left side's sidepiece of above-mentioned gearbox at the recess sidepiece of above-mentioned transmission shaft,

The power of the output shaft of the stepless speed changes devices of the above-mentioned usefulness of advancing is passed to the right side and left lateral motion device via input shaft, driving gear, transmission shaft, the right side and left side clutch.

2. the drive mechanism of advancing of operating vehicle as claimed in claim 1, the input shaft of the stepless speed changes devices of the above-mentioned usefulness of advancing is provided in the recess side, and extends to the input shaft side.

3. the drive mechanism of advancing of an operating vehicle, with the power of motor via the stepless speed changes devices of the usefulness of advancing and gearbox and be passed to the right side and left lateral motion device,

At the right or left recess that side's sidepiece forms to the right or left the opposing party's side enters of above-mentioned gearbox, input shaft is equipped with in right or left the opposing party's sidepiece of the gearbox adjacent, with above-mentioned recess,

At the advance stepless speed changes devices of usefulness of the recess place of above-mentioned gearbox configuration, the output shaft of the stepless speed changes devices of the above-mentioned usefulness of advancing is provided in the recess side of above-mentioned gearbox and links with the input shaft interlock,

It is, adjacent with the recess of above-mentioned gearbox and be supported with transmission shaft from right or left side's side of above-mentioned gearbox to the opposing party's side,

The recess sidepiece of above-mentioned transmission shaft be equipped with can with the transmission of power of and low speed identical with side's direction of the moving device on the above-mentioned right side or a left side to the opposing party's of right or left moving device friction multi-plate shallow turn clutch,

Being equipped with at the input shaft sidepiece of above-mentioned transmission shaft can be with the friction multi-plate reversing clutch of the transmission of power opposite with side's direction of the moving device on the above-mentioned right side or a left side to the opposing party of right or left moving device,

The power of the output shaft of the stepless speed changes devices of the above-mentioned usefulness of advancing is passed to from above-mentioned input shaft and shallows turn clutch and reversing clutch.

4. the drive mechanism of advancing of operating vehicle as claimed in claim 3,

Be supported with other transmission shaft from right or left side's sidepiece of above-mentioned gearbox to the opposing party's sidepiece, on other transmission shaft, possess transmission of power to the above-mentioned right side and the right and left output gear of left lateral motion device, and,

The power of above-mentioned input shaft is passed to other transmission shaft via driving gear, be passed to via driving gear from above-mentioned other transmission shaft and shallow turn clutch, is passed to the right side or left output gear from the above-mentioned clutch of shallowing turn,

The power of above-mentioned input shaft is passed to reversing clutch via driving gear, be passed to the right side or left output gear from above-mentioned reversing clutch.

5. the drive mechanism of advancing of operating vehicle as claimed in claim 2,

On the recess sidepiece of other transmission shaft, be equipped with the above-mentioned right side and left output gear,

On the input shaft sidepiece of above-mentioned gearbox, be equipped with the transmission of power of above-mentioned input shaft to the driving gear of other transmission shaft and with the transmission of power of above-mentioned input shaft driving gear to reversing clutch.

6. combine-harvester,

Dress is advanced in the front portion of body is equipped with, and speed change is used or the gearbox of the hydraulic mechanism of turning usefulness, and,

Drive Section is provided in a right or left side's of above-mentioned gearbox lateral outer side, supports the lateral outer side that the supporting frame of reaping part is provided in right or left the opposing party of above-mentioned gearbox freely swinging up and down driving,

To have to above-mentioned hydraulic mechanism is provided in the horizontal sidepiece of the supporting frame side of above-mentioned gearbox for the hydraulic unit of the control valve of row's operation element oil.

7. combine-harvester as claimed in claim 6 is characterized in that,

Left and right directions upper support in the inside of gearbox is used to support the transmission shaft of above-mentioned hydraulic mechanism, and the end of above-mentioned transmission shaft is inserted into the inside of above-mentioned hydraulic unit,

Be equipped with from the oil circuit of above-mentioned hydraulic mechanism in the inside of above-mentioned transmission shaft, carry out the row's of giving operation of working oil from above-mentioned hydraulic unit via the oil circuit of transmission shaft to hydraulic mechanism up to the end of above-mentioned transmission shaft.

8. the speed changing structure of advancing of an operating vehicle,

Be provided with and comprise the hydraulic type pump that can infinitely change capacity, and accept from the working oil of above-mentioned hydraulic type pump and the main transformer quick-mounting of the continuously variable of driven hydraulic motor is put, being provided with the output variable speed that will put from above-mentioned main transformer quick-mounting is the multistage secondary gear of gear type

The main transformer speed operation piece of change being regulated above-mentioned hydraulic type pump is configured in the riding manipulation space, is configured in outside the riding manipulation space switching the secondary variable speed operation spare of regulating the secondary gear of said gear formula.

9. the speed changing structure of advancing of operating vehicle as claimed in claim 8 constitutes the capacity that can change above-mentioned hydraulic motor.

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