CN102849135B - Crawler belt stretch adjusting device - Google Patents

Abstract

A kind of crawler belt stretch adjusting device is provided, the Operation Van comprising crawler belt stretch adjusting device has to the right and left moving device provides the 1st and the 2nd turning mechanism of velocity contrast, improve the turning performance of steering operation structure and the operability of cornering operation.It is corresponding with the unit operation amount of steering operation part (77), poor based on the unit velocity of the 1st turning mechanism (the 2nd turning mechanism) to be configured to, medium and small in the region of straight position (N) side of steering operation part, large in the region of the steering lock side of steering operation part (77).The variation characteristic of the unit velocity difference of the variation characteristic of the unit velocity difference of the 1st state and the 2nd state is set as different variation characteristics.

Description

Crawler belt stretch adjusting device

The divisional application that the application is the applying date is on September 25th, 2008, application number is 200810149742.5, denomination of invention is the patent application of Operation Van

Technical field

The present invention relates to and a kind of there is Operation Van that is right and left moving device, more specifically, relate to a kind of steering operation structure of Operation Van, to the right and left moving device apply velocity contrast and carry out the steering operation of body.

Background technology

In the combination machine of the example as Operation Van, disclosed in JP2000-335268A, have: right and left moving device (1 of Fig. 1 and Fig. 2); 1st turning mechanism (45 of Fig. 2), to the right and left moving device apply velocity contrast and body is turned; 2nd turning mechanism (49,50 of Fig. 2), to the right and left moving device apply the velocity contrast larger than the 1st turning mechanism and body is turned.

In JP2000-335268A, have: turning set mechanism (71,55 of Fig. 3), the 1st state of the 1st turning mechanism work or the 2nd state of the 2nd turning mechanism work can be set; Steering operation part (58 of Fig. 4), can operate artificially.

Thus, when steering operation part is operated into straight position, to the right and left moving device transmit the power of identical speed and equidirectional, thus body is straight.

In the 1st state, if steering operation part is such as operated to the right, then the 1st turning mechanism becomes mode of operation, utilize velocity contrast that is right and left moving device, body is made to change direction to the right, steering operation part is operated larger to the right, and the velocity contrast of right and left moving device is larger, and body changes direction to the right with less turn radius.In the 2nd state, if steering operation part is such as operated to the right, then the 2nd turning mechanism becomes mode of operation, and same as described above, body also changes direction to the right.

As JP2000-335268A, when having to the right and left moving device applies the 1st and the 2nd turning mechanism of velocity contrast, the operability of turning performance and cornering operation raising in there is room for improvement.

Summary of the invention

The object of the invention is to, in the steering operation structure of Operation Van, when having to the right and left moving device applies the 1st and the 2nd turning mechanism of velocity contrast and has the turning set mechanism that can set the 1st state of the 1st turning mechanism work or the 2nd state of the 2nd turning mechanism work, realize the raising of the turning performance of Operation Van and the operability of cornering operation.

In order to reach above-mentioned purpose, the 1st latent structure of Operation Van of the present invention is to form steering operation structure as follows.

Have: right and left moving device; 1st turning mechanism, to the right and left moving device apply velocity contrast and body is turned; 2nd turning mechanism, to the right and left moving device apply the velocity contrast larger than the 1st turning mechanism and body is turned.

Have: turning set mechanism, the 1st state of the 1st turning mechanism work or the 2nd state of the 2nd turning mechanism work can be set; Steering operation part, can operate artificially.

There is control mechanism, in the 1st state, with steering operation part from straight position more by the right or left operation, mode that the velocity contrast of the right side and left moving device is larger operate the 1st turning mechanism, in the 2nd state, with steering operation part from straight position more by the right or left operation, mode that the velocity contrast of the right side and left moving device is larger operate the 2nd turning mechanism.

In the 1st state, corresponding with the unit operation amount of steering operation part, poor based on the unit velocity of the 1st turning mechanism, be configured to medium and small in the region of the straight position side of steering operation part, large in the region of the steering lock side of steering operation part.

In the 2nd state, corresponding with the unit operation amount of steering operation part, poor based on the unit velocity of the 2nd turning mechanism, be configured to medium and small in the region of the straight position side of steering operation part, large in the region of the steering lock side of steering operation part.

The variation characteristic of the unit velocity difference of the variation characteristic of the unit velocity difference of the 1st state and the 2nd state is set as different variation characteristics.

According to above-mentioned 1st feature structure, in the 1st state (the 2nd state), if steering operation part is (left side) operation by the right, then the 1st turning mechanism (the 2nd turning mechanism) becomes mode of operation, by velocity contrast that is right and left moving device, make body (left side) change direction to the right, (left side) operation is larger by the right for steering operation part, the velocity contrast of right and left moving device is larger, makes body with little turn radius (left side) change direction to the right.

Now, operate in the region of straight position side steering operation part state (from straight position only a little to the right or the state of left operation steering operation part), the velocity contrast of right and left moving device is smaller, become in the operation of steering operation part ratio body more to the right (left side) change nyctitropic state, so the state that the inching being applicable to the direction of body when carrying out straight is such.This is specially adapted to the 1st state.

In addition, operate in the region of steering lock side steering operation part state (from straight position to the right or a left side significantly operate the state of steering operation part), the velocity contrast of right and left moving device is larger, become in the operation of steering operation part ratio body with little turn radius to the right (left side) change nyctitropic state, so be applicable to the state in the direction changing body hastily.This is specially adapted to the 2nd state.

And then, according to above-mentioned 1st feature structure, the variation characteristic of the unit velocity difference of the variation characteristic of the unit velocity difference of the 1st state and the 2nd state is set as different variation characteristics.

Thus, a situation arises (occurrence features) for the right side from straight position to steering lock during operation steering operation part and the velocity contrast of left moving device, different in the 1st and the 2nd state, so, compared with velocity contrast above-mentioned in the 1st and the 2nd state a situation arises (occurrence features) identical formation, the difference of the turning performance of the 1st and the 2nd state is larger, is easy to corresponding with the state on operation ground or operation form and sets the 1st and the 2nd suitable state.

Therefore, in the 1st and the 2nd state, the unit velocity based on 1st and 2nd turning mechanism corresponding with the unit operation amount of steering operation part is poor, less in the region of the straight position side of steering operation part, larger in the region of the steering lock side of steering operation part, and, differing greatly of the turning performance of the 1st and the 2nd state, from above-mentioned 2 points, be easy to corresponding with the state on operation ground or mode of operation and set the 1st and the 2nd suitable state, the lifting of the turning performance of Operation Van and the operability of cornering operation can be realized.

In the 2nd feature structure of the present invention, in the region of the straight position side of steering operation part, set the variation characteristic of the unit velocity difference of the 1st and the 2nd state in the mode that the unit velocity of the 1st state difference is less than the unit velocity difference of the 2nd state.This is more favourable in following.

In the 1st state, operate in the region of straight position side steering operation part state (from straight position only a little to the right or the state of left operation steering operation part), the velocity contrast of right and left moving device is smaller, become the ratio of the operation in steering operation part, body more to the right (left side) changes nyctitropic state, so be applicable to the state of the inching in the direction of body when carrying out straight.

Now, according to above-mentioned 2nd feature structure, to the right and in left moving device the 1st state that applies smaller velocity contrast and make body turn, state as described above can be obtained, so, the inching in the 1st state and the direction of body time straight is consistent in characteristic (direction of body not too large the characteristic that changes), the inching in the direction of body when can not carry out straight with having not harmony sense for chaufeur.

Therefore, it is possible to make the turning performance of Operation Van and the operability of cornering operation more improve.

In the 3rd feature structure of the present invention, 1st turning mechanism shallows turn mechanism (grandturnmechanism), this shallow turn mechanism to the right or the opposing party of left moving device transmit and the power of low speed identical with the right side or a side direction of left moving device, the 2nd turning mechanism be to the right or left moving device carry out the stop mechanism braked.

In the 4th feature structure of the present invention, 1st turning mechanism shallows turn mechanism, this shallow turn mechanism to the right or the opposing party of left moving device transmit and the power of low speed identical with the right side or a side direction of left moving device, 2nd turning mechanism is reversing device, this reversing device to the right or the opposing party of left moving device transmit the power contrary with the right side or a side direction of left moving device.

If also there is above-mentioned 3rd feature structure or the 4th feature structure except having the 2nd feature structure, then by shallowing turn mechanism and stop mechanism or reversing device, the turning performance of the 1st and the 2nd state can be made completely different, so be easy to corresponding with the state on operation ground or mode of operation and set the 1st and the 2nd suitable state.

Therefore, the difference of the turning performance of the 1st and the 2nd state is increased, be easy to corresponding with the state on operation ground or mode of operation and set the 1st and the 2nd suitable state, the raising of the turning performance of Operation Van and the operability of cornering operation can be realized.

In the 5th feature structure of the present invention, except above-mentioned 2nd feature structure, also there is following formation like that.

1st turning mechanism shallows turn mechanism, this shallow turn mechanism to the right or the opposing party of left moving device transmit and the power of low speed identical with the right side or a side direction of left moving device, the 2nd turning mechanism be to the right or left moving device carry out the stop mechanism braked.There is reversing device, this reversing device to the right or the opposing party of left moving device transmit the power contrary with the right side or a side direction of left moving device.

Be configured to utilize turning set mechanism to set and use the 1st state of shallowing turn mechanism, the 2nd state using stop mechanism, use the 3rd state of reversing device.In the region of the straight position side of steering operation part, set the variation characteristic of the unit velocity difference of the 2nd and the 3rd state in the mode that the unit velocity of the 2nd state difference is less than the unit velocity difference of the 3rd state.

If based on above-mentioned 5th feature structure, then shallow turn mechanism, stop mechanism and reversing device by having, can make the 1st, 2, the turning performance of 3 states is completely different, so with the state on operation ground or mode of operation is corresponding and options expands, be easy to setting suitable the 1st, 2,3 states.

In addition, in the region of the straight position side of steering operation part, the unit velocity difference of the 1st state is set to poor less than the unit velocity of the 2nd state, the unit velocity difference of the 2nd state is set to poor less than the unit velocity of the 3rd state, the 1st, 2, the variation characteristic of the unit velocity difference of 3 states is set to different.Thus, make the 1st, 2, the differing greatly of the turning performance of 3 states, with the state on operation ground or mode of operation is corresponding and options expands, be easy to setting suitable the 1st, 2,3 states.

Therefore, by by the 1st, 2,3 states make options expand this point and make the 1st, 2, the difference of the turning performance of 3 states increases this point, be easy to corresponding with the state on operation ground or mode of operation and set suitable 1st, 2,3 states, the raising of the turning performance of Operation Van and the operability of cornering operation can be realized.

In the 6th feature structure of the present invention, except above-mentioned 2nd feature structure, also there is following formation like that.

1st turning mechanism shallows turn mechanism, this shallow turn mechanism to the right or the opposing party of left moving device transmit and the power of low speed identical with the right side or a side direction of left moving device, the 2nd turning mechanism be to the right or left moving device carry out the stop mechanism braked.There is reversing device, this reversing device to the right or the opposing party of left moving device transmit the power contrary with the right side or a side direction of left moving device.

Be configured to can utilize turning set mechanism to set the 3rd state using the 1st state of shallowing turn mechanism, the 2nd state using stop mechanism, use reversing device.In the region of the straight position side of steering operation part, set the variation characteristic of the unit velocity difference of the 2nd and the 3rd state in the unit velocity of the 2nd state difference mode identical with the unit velocity of the 3rd state.

If based on above-mentioned 6th feature structure, then shallow turn mechanism, stop mechanism and reversing device by having, can make the 1st, 2, the turning performance of 3 states is completely different, so with the state on operation ground or mode of operation is corresponding and options expands, be easy to setting suitable the 1st, 2,3 states.

In addition, in the region of the straight position side of steering operation part, the unit velocity difference of the 1st state is set to poor less than the unit velocity of the 2nd state, and the unit velocity difference of the 2nd state and the unit velocity difference of the 3rd state are set to identical velocity contrast.Thus, can not make the 1st, 2, the difference of the turning performance of 3 states becomes unnecessary large, be easy to corresponding with the state on operation ground or mode of operation and set suitable 1st, 2,3 states.

Therefore, by by the 1st, 2,3 states make options expand this point, and do not make the 1st, 2, the difference of the turning performance of 3 states becomes unnecessary large this point, be easy to corresponding with the state on operation ground and mode of operation and set suitable 1st, 2,3 states, the raising of the turning performance of Operation Van and the operability of cornering operation can be realized.

While read on one side following explanation with reference to accompanying drawing thus clear and definite other feature structure and advantage.

In the following description, express as long as no different, then be called fore-and-aft direction using the direction of the combination machine of the example as Operation Van forwards straight (advance) as benchmark, horizontal direction with this fore-and-aft direction orthogonal 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.

Accompanying drawing explanation

Fig. 1 ~ Fig. 6 is the figure representing the 1st embodiment.

Fig. 1 is the unitary side view of combination machine.

Fig. 2 is the vertical profile front view of change speed gear box, the right side and Left Drive case.

Fig. 3 is the vertical profile front view of vicinity of shallowing turn power-transfer clutch (grandturnclutch), drg, reversing clutch, the right side and left side clutch of change speed gear box.

Fig. 4 is the figure of the hydraulic circuit structure represented in hydraulic pressure unit.

Fig. 5 is the figure of the relation representing shifter bar, deflecting bar, cornering mode switch, hydrostatic continuously variable unit and hydraulic pressure unit.

Fig. 6 is the figure representing following solid line, namely the solid line (shallowing turn (grandturn)) of the relation of the operating position of deflecting bar and the actuating current (shallowing turn the operation pressure of power-transfer clutch) of proportional control valve is represented, represent the solid line (wheel one stops one turn of pivot turn (pivotturn)) of the relation of the operating position of deflecting bar and the actuating current (operation pressure of drg) of proportional control valve, represent the solid line (wheel a positive and a negative pivot turn (spinturn)) of the relation of the operating position of deflecting bar and the actuating current (operation pressure of reversing clutch) of proportional control valve.

Fig. 7 ~ Figure 16 is the figure representing the 2nd embodiment.

Fig. 7 is the lateral plan of working rig.

Fig. 8 is the lateral plan of crawler travel device.

Fig. 9 is the birds-eye view of crawler travel device.

Figure 10 is the lateral plan at crawler travel device rear portion.

Figure 11 is the vertical profile birds-eye view of crawler belt stretch adjusting device.

Figure 12 is the longitudinal cross-sectional side view of crawler belt stretch adjusting device.

Figure 13 is the birds-eye view of protruding guiding element installation constitution.

Figure 14 is the block diagram of protruding guiding element installation portion and link.

Figure 15 is the birds-eye view of wheel body support.

Figure 16 is the lateral plan of wheel body support.

Figure 17 ~ 35 are the figure representing the 3rd embodiment.

Figure 17 is the unitary side view of combination machine.

Figure 18 is the lateral plan of cereal box.

Figure 19 is the birds-eye view of cereal box.

Figure 20 is the block diagram of cereal box viewed from front inside body.

Figure 21 is the skeleton diagram of driving system.

Figure 22 is the longitudinal cross-sectional side view of the connecting structure representing end screw rod and vertical conveyer.

Figure 23 is the expansion section-drawing of the bindiny mechanism representing vertical conveyer and horizontal conveyer.

Figure 24 is the back view of cereal box.

Figure 25 represents that threshing transports the birds-eye view of the turning driving structure of device.

Figure 26 is the back view in the portion that transports representing cereal box.

Figure 27 is the block diagram at the rear portion representing cereal box.

Figure 28 represents that the movable hood of cereal box bottom is by the block diagram of open state.

Figure 29 represents the cross-sectional plan view from driving engine to the power-transfer clutch on-state of the driving system of end screw rod.

Figure 30 represents the cross-sectional plan view from driving engine to the power-transfer clutch dissengaged positions of the driving system of end screw rod.

Figure 31 is the longitudinal cross-sectional side view of the drive structure representing screw front end portion, the end.

Figure 32 is the front view representing the driving structure flowing down directing plate.

Figure 33 be clutch components from the front view viewed from axis direction.

Figure 34 is the section-drawing of clutch components.

Figure 35 is the expansion drawing of the engaging recessed part represented in clutch components.

Detailed description of the invention

Hereinafter, with reference to the accompanying drawings of embodiments of the present invention.Following illustrate multiple embodiment, but think that the combination of feature of other embodiments of characteristic sum of one of them embodiment is also contained within scope of the present invention.

[the 1st embodiment]

[1]

As shown in Figure 1, moving device is being equivalent to by right and left crawler travel device 1() front portion of body of supporting, lifting freely support around transverse axis core P1 and extract framework 2, there is lifting and drive and extract the lifting pressure cylinder 3 of framework 2, be supported with the portion of extracting 4 extracting on framework 2.On the right side of the front portion of body, there is Drive Section 5, in the left side at the rear portion of body, there is sheller unit 8, on the right side at the rear portion of body, there is cereal box 9, form the combination machine from off-type of the example as Operation Van.

Then, change speed gear box 10 is described.

As shown in Figures 1 and 2, near the left and right central authorities of the front portion of body, there is change speed gear box 10, be formed with the recess 10a of ladder difference shape on the top of the right side of change speed gear box 10, be linked with hydrostatic stepless speed change device 11 in the mode of the recess 10a entering into change speed gear box 10.Have right and left support 10b in the outside of the bottom of change speed gear box 10, the right side and the left support 10b of the right side and Left Drive case 14 and change speed gear box 10 link and stretch out to front side.

As shown in Figure 1 and Figure 2, right and left axle box 15 and right and Left Drive case 14 link and to the right and left side stretch out, on the right and right side of left axle box 15 and the end in left side, there is the sprocket wheel 1a driving right and left crawler travel device 1.In the outside of the bottom of change speed gear box 10, there is connecting part 10c, from the connecting part 10c of change speed gear box 10 until right and Left Drive case 14, be linked with link 13.

[2]

Then, the structure of the driving system (straight system) in change speed gear box 10 is described.

As shown in Figure 2, the power of driving engine (not shown) is via driving band (not shown), and be passed to the input shaft (not shown) of hydrostatic stepless speed change device 11, the output shaft 11a of hydrostatic stepless speed change device 11 is inserted into the inside of change speed gear box 10.Input shaft 22 is supported in the top of change speed gear box 10, and transmission gear 23,24 is fixed on input shaft 22, the output shaft 11a of hydrostatic stepless speed change device 11 by spline structure with transmission gear 24(input shaft 22) link.

As shown in Figure 2, on transmission shaft 27 on the top being bearing in change speed gear box 10, high speed gear 25 and low speed gear 26 is embedded with relatively rotatably, transmission gear 23 and high speed gear 25 engage, transmission gear 24 and low speed gear 26 engage, and gearshift parts 28 rotate integrally by spline structure and sliding freely fitted on transmission shaft 27.By transmission gear 23 and high speed gear 25, transmission gear 24 and low speed gear 26, gearshift parts 28 and form secondary speed-changing device, by make gearshift parts 28 with at a high speed and low speed gear 25,26 engage, the power of input shaft 27 can speed change be just two-stage (high speed position and low-speed position) and be passed to transmission shaft 27.Usually, to shift gears parts 28 to the position slide engaged with high speed gear 25, thus setting high-speed position.

As shown in FIG. 2 and 3, along the lower support transmission shaft 29 of change speed gear box 10, the left side of transmission shaft 29 is fixed with transmission gear 31, the left side of transmission shaft 27 is fixed with transmission gear 30, transmission gear 30,31 engages.Transmission shaft 29 is rotatably embedded with right and left output gear 32R, 32L outward relatively, on the right side and left side of right and left output gear 32R, 32L, right and left engaging piece 33R, 33L rotate integrally by spline structure and sliding freely fitted on transmission shaft 29.Between right output gear 32R and right engaging piece 33R, form right side clutch 34, between left output gear 32L and left engaging piece 33L, form left side clutch 34.

As shown in Figure 2, from the right side of change speed gear box 10 and left support 10b until right and Left Drive case 14 is supported with transmission shaft 35, in the inside of change speed gear box 10, the transmission gear 36 be fixed on transmission shaft 35 engages with right and left output gear 32R, 32L, in inside that is right and Left Drive case 14, transmission gear 37 is fixed on transmission shaft 35.From the right side and Left Drive case 14 until right and left axle box 15, be supported with right and left axletree 38, in inside that is right and Left Drive case 14, the transmission gear 39 be fixed on right and left axletree 38 engages with transmission gear 37.In inside that is right and left axle box 15, right and left axletree 38 to the right and left side stretch out, the sprocket wheel 1a(of right and left crawler travel device 1 is with reference to Fig. 1), link with the right and right side of left axletree 38 and the end in left side.

Based on above structure, as shown in Figure 2, the power of input shaft 22 via transmission shaft 27, transmission gear 30,31, transmission shaft 29, right and left side clutch 34(is right and left engaging piece 33R, 33L), right and left output gear 32R, 32L, transmission gear 36, transmission shaft 35, transmission gear 37,39, right and left axletree 38, be passed to right and left crawler travel device 1, thus body is straight.

[3]

Then, right and left side clutch 34 are described.

As shown in Figure 3, the right side of transmission shaft 29 and the outside face of left side are formed with spline part 29a, right and left engaging piece 33R, 33L can rotate integrally and freely slidably fitted on the spline part 29a of transmission shaft 29, accepting parts 40 can integrally rotatably fitted on the spline part 29a of transmission shaft 29.

As shown in Figure 3, on the position of undertaking parts 40 side of right and left engaging piece 33R, 33L, circumferentially configure multiple recess, right and left engaging piece 33R, 33L recess respective on, spring 41 is configured with doubly in inner side and outer side, by undertaking parts 40 and spring 41, right and left engaging piece 33R, 33L to the right and the engagement side of left output gear 32R, 32L exerted a force.Engaged with right and left output gear 32R, 32L by right and left engaging piece 33R, 33L, become drive state that is right and left side clutch 34, the power of transmission shaft 29 is passed to right and left crawler travel device 1 via the right side and left side clutch 34.

As shown in Figure 3, piston 42 can be configured in right and between left output gear 32R, 32L and transmission shaft 29 freely slidably, piston 42 abuts with right and left engaging piece 33R, 33L, stride across right and left engaging piece 33R, 33L until piston 42 and be inserted with spring pin 43, rotate integratedly with right and left engaging piece 33R, 33L to make piston 42.

As shown in Figure 3, if supply action oil to the right and between left output gear 32R, 32L and piston 42, then right and left engaging piece 33R, 33L and piston 42 overcome spring 41 and are left side by slide to right and left output gear 32R, 32L, become the dissengaged positions of the right side and left side clutch 34.If from right and discharging operation oil between left output gear 32R, 32L and piston 42, then right and left engaging piece 33R, 33L and piston 42 under the effect of spring 41 by slide to right and left output gear 32R, 32L engagement side, become the drive state of the right side and left side clutch 34.

[4]

Then, the structure of the driving system (turning system) in change speed gear box 10 is described.

As shown in Figures 2 and 3, transmission shaft 44 is supported with across change speed gear box 10, relatively rotatably engage with the gear part of the peripheral part of right engaging piece 33R fitted in the transmission gear 45 of the right side of transmission shaft 44, have between transmission shaft 44 and transmission gear 45 and shallow turn power-transfer clutch 46(and be equivalent to the 1st turning mechanism, and be equivalent to shallow turn mechanism (grandturnmechanism)).Shallowing turn power-transfer clutch 46, to be configured to friction multi-plate, by supply working oil and be operating as drive state, is operating as dissengaged positions by discharging working oil.

As shown in Figures 2 and 3, turning clutch case 47, relatively rotatably fitted on transmission shaft 29, is fixed on the transmission gear 48 on transmission shaft 44 and engages with the transmission gear 47a of the peripheral part of turning clutch case 47.Turning clutch case 47 is configured to symmetrical, at turning clutch case 47 with right and leftly have the right side and turnon left power-transfer clutch 49 between output gear 32R, 32L.It is multi-plate that right and turnon left power-transfer clutch 49 is configured to friction, is operating as drive state by supply working oil.In this case, in the right side and turnon left power-transfer clutch 49, friction plate closely configures mutually, even if working oil is discharged, right and turnon left power-transfer clutch 49 also becomes half drive state.

Thus, as shown in Figures 2 and 3, shallow turn power-transfer clutch 46 when being operating as drive state, the power of transmission shaft 29 via right engaging piece 33R, transmission gear 45, shallow turn power-transfer clutch 46, transmission shaft 44 and transmission gear 48, as identical with transmission shaft 29 hand of rotation and than transmission shaft 29 low speed power and be passed to turning clutch case 47.When the right side or left side clutch 34 being operating as dissengaged positions, the right side or turnon left power-transfer clutch 49 being operating as drive state, identical with transmission shaft 29 hand of rotation and be passed to right or left output gear 32R, 32L than the power of transmission shaft 29 low speed.

As shown in Figures 2 and 3, there is drg 50(in the left side of transmission shaft 44 and be equivalent to the 2nd turning mechanism) (being equivalent to stop mechanism).It is multi-plate that drg 50 is configured to friction, is operating as braking mode by supply working oil, is operating as disarm state by discharging working oil.

Thus, as shown in Figures 2 and 3, when drg 50 is operating as braking mode, via transmission shaft 44 and transmission gear 48, turning clutch case 47 becomes braking mode.Right or left side clutch 34 be operating as dissengaged positions, the right side or turnon left power-transfer clutch 49 be operating as drive state time, right or left output gear 32R, 32L become braking mode.

As shown in Figures 2 and 3, the left side of transmission shaft 27 is fixed with transmission gear 51, the left side of transmission shaft 44 is rotatably embedded with transmission gear 52 outward relatively, transmission gear 51,52 engages, and has reversing clutch 53(and be equivalent to the 2nd turning mechanism between transmission shaft 44 and transmission gear 52) (being equivalent to reversing device).It is multi-plate that reversing clutch 53 is configured to friction, is operating as drive state by supply working oil, is operating as dissengaged positions by discharging working oil.

Thus, as shown in Figures 2 and 3, when reversing clutch 53 is operating as drive state, the power of transmission shaft 27 via transmission gear 51,52, reversing clutch 53, transmission shaft 44 and transmission gear 48, be passed to turning clutch case 47 as the power contrary with transmission shaft 29 hand of rotation.Right or left side clutch 34 be operating as dissengaged positions, right side or turnon left power-transfer clutch 49 be operating as drive state time, be passed to the right side or left output gear 32R, 32L with the power of the rightabout rotation of transmission shaft 29.

[5]

Then, the operation of hydrostatic continuously variable unit 11 is described.

As shown in Figure 5, the pump 11P of hydrostatic continuously variable unit 11 be configured to center position N, the F that to march forward from center position N high-speed side and retreat the high-speed side stepless change freely of R, the motor 11M of hydrostatic continuously variable unit 11 is configured to height two-stage ground speed change freely.Have the hydraulic actuating cylinder 59 of swash plate, the control cock 60 to hydraulic actuating cylinder 59 discharge operation element oil of the pump 11P of operation hydrostatic continuously variable unit 11, the shifter bar 61 and the control cock 60 that are provided in Drive Section 5 are mechanically connected.Thus, by operation shifter bar 61, control cock 60 is operated, hydraulic actuating cylinder 59 action, and the swash plate of the pump 11P of hydrostatic continuously variable unit 11 is operated to the position corresponding with the operating position of shifter bar 61.

As shown in Figure 5, possess the hydraulic actuating cylinder 62 of swash plate, the control cock 63 to the solenoid operated of hydraulic actuating cylinder 62 discharge operation element oil of the motor 11M of operation hydrostatic continuously variable unit 11, the grip part of shifter bar 61 possesses varying speed switch 61a, and the operation signal of the varying speed switch 61a of shifter bar 61 is input to control setup 64(and is equivalent to control mechanism) in.Thus, by operating the varying speed switch 61a of shifter bar 61, control cock 63 controlled device 64 operates, hydraulic actuating cylinder 62 action, and the swash plate of the motor 11M of hydrostatic continuously variable unit 11 is operated at a high speed and low-speed position.

The cornering mode switch 78 recorded in [7] described later [8] [9] [10], shallow turn (grandturn), wheel one stops in each state of one turn of pivot turn (pivotturn) and wheel a positive and a negative pivot turn (spinturn), can select to shallow turn state by cornering mode switch 78, wheel one stops one turn of pivot turn state and wheel a positive and a negative pivot turn state, is utilize the varying speed switch 61a of shifter bar 61 that the swash plate of the motor 11M of hydrostatic continuously variable unit 11 is operated the state of low-speed position.If utilize the varying speed switch 61a of shifter bar 61 and the swash plate of the motor 11M of hydrostatic continuously variable unit 11 operated the state of high speed position, then have nothing to do with the operating position of cornering mode switch 78, select to shallow turn state.

[6]

Then, illustrate to the right and left side clutch 34(is right and left engaging piece 33R, 33L), right and turnon left power-transfer clutch 49, shallow turn the hydraulic pressure unit 57 of power-transfer clutch 46, drg 50, reversing clutch 53 discharge operation element oil.

As shown in Figure 4, on the input shaft (not shown) of hydrostatic continuously variable unit 11, be linked with charge pump (not shown) and Hydraulic Pump 56, be configured to the input shaft by hydrostatic stepless speed change device 11, drive charge pump and Hydraulic Pump 56, the working oil of charge pump is supplied to hydrostatic continuously variable unit 11.As shown in FIG. 2 and 3, hydraulic pressure unit 57 links with the outside face of the left horizontal sidepiece of change speed gear box 10, and the outside pipe arrangement 58(of self-hydraulic pump 56 is with reference to Fig. 4) be connected with hydraulic pressure unit 57.

As shown in FIG. 2 and 3, the left cross side of the through change speed gear box in left part 10 of transmission shaft 29,44, and be inserted into the inside of hydraulic pressure unit 57, from the left part of transmission shaft 29 until right and left side clutch 34(is right and left engaging piece 33R, 33L), right and turnon left power-transfer clutch 49, possess oil circuit 29b in the inside of transmission shaft 29.From the left part of transmission shaft 44 until shallow turn power-transfer clutch 46 and reversing clutch 53, possesses oil circuit 44a in the inside of transmission shaft 44.In the inside of hydraulic pressure unit 57, possesses drg 50 in the end of transmission shaft 44.

As shown in Figure 4, in the inside of hydraulic pressure unit 57, possess right-hand corner control cock 67, turnon left control cock 68, safety valve 69, unloading valve 70, proportional control valve 71, turning switching control valve 72, guide operating valve 73,74.The outside pipe arrangement 58 of self-hydraulic pump 56 is connected with hydraulic pressure unit 57, the link surface (faying face) of the left horizontal sidepiece of hydraulic pressure unit 57 and change speed gear box 10 is formed with multiple oil circuit (not shown), right and turnon left control cock 67,68, safety valve 69, unloading valve 70 be connected to side by side via the oil circuit of link surface (faying face) on the oil circuit 66 that is connected with outside pipe arrangement 58.The link surface (faying face) of the left horizontal sidepiece of hydraulic pressure unit 57 and change speed gear box 10 is formed with discharge oil circuit, and the working oil of safety valve 69 and unloading valve 70 is back to change speed gear box 10 via above-mentioned discharge oil circuit.

As shown in Figure 2, the oil circuit of right-hand corner control cock 67 via link surface (faying face) and the oil circuit 29b of transmission shaft 29, engaging piece 33R right with right side clutch 34() and right-hand corner power-transfer clutch 49 be connected.The oil circuit of turnon left control cock 68 via link surface (faying face) and the oil circuit 29b of transmission shaft 29, engaging piece 33L left with left side clutch 34() and turnon left power-transfer clutch 49 be connected.

As shown in Figure 4, right and turnon left control cock 67,68 is configured to the solenoid operated that freely can operate supply position 67a, 68a and drain position 67b, 68b, exerts a force to drain position 67b, 68b.Unloading valve 70 is configured to the solenoid operated that freely can operate off-position 70a and drain position 70b, exerts a force to off-position 70a.From on oil circuit 75 that is right and branch between turnon left control cock 67,68 and the oil circuit 29b of transmission shaft 29, be connected in series proportional control cock 71 and turning switching control valve 72, the oil circuit of turning switching control valve 72 via link surface (faying face) and the oil circuit 44a of transmission shaft 44, with shallow turn power-transfer clutch 46 and reversing clutch 53 is connected, turning switching control valve 72 is connected with drg 50 via the oil circuit 76 of hydraulic pressure unit 57.

As shown in Figure 4, proportional control valve 71 is configured to solenoid operated, can carry out the flow control (Stress control) of working oil.Turning switching control valve 72 be configured to freely to operate shallow turn position 72a, pilot operated that wheel one stops one turn of pivot turn position 72b and wheel a positive and a negative pivot turn position 72c, exert a force to shallowing turn position 72a.The mode that operation stops one turn of pivot turn position 72b to wheel one the guide's working oil from oil circuit 75 branch to be supplied to turning switching control valve 72 is formed guide operating valve 73, and the mode operating wheel a positive and a negative pivot turn position 72c the guide's working oil from oil circuit 75 branch to be supplied to turning switching control valve 72 is formed guide operating valve 74.

Right and turnon left control cock 67,68, unloading valve 70, proportional control valve 71, guide operating valve 73,74, operated by control setup 64 as described in [7] described later [8] [9] [10].

[7]

Then, the straight moving condition based on deflecting bar 77 is described.

As shown in Figure 5, at Drive Section 5(with reference to Fig. 1) in be equipped with to the right and deflecting bar 77(that a left side operates freely is artificially equivalent to steering operation part), the operating position of deflecting bar 77 is input in control setup 64, and deflecting bar 77 is configured to operate straight position N, the right side and left 1st turning position R1, L1, the right side and left 2nd turning position R2, L2 freely.In Drive Section 5, be equipped with cornering mode switch 78(be equivalent to turning set mechanism), the operating position of cornering mode switch 78 is input in control setup 64, cornering mode switch 78 possess shallow turn position (being equivalent to the 1st state), wheel one stops one turn of pivot turn position (being equivalent to the 2nd state) and wheel a positive and a negative pivot turn position (being equivalent to the 2nd and the 3rd state).

As shown in Figures 4 and 5, have nothing to do with the operating position of cornering mode switch 78, if deflecting bar 77 is operated into straight position N, then right and turnon left control cock 67,68 is operated into drain position 67b, 68b, unloading valve 70 is operated into drain position 70b, working oil is from right and left side clutch 34(right and left engaging piece 33R, 33L), right and turnon left power-transfer clutch 49 discharges, right and left side clutch 34(right and left engaging piece 33R, 33L) be operating as drive state, right and turnon left power-transfer clutch 49 is operating as half drive state.Shallow turn and reversing clutch 46,53 is operating as dissengaged positions by proportional control valve 71, drg 50 is operating as disarm state.

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

[8]

Then, illustrate and shallow turn state based on deflecting bar 77.

As shown in Figures 4 and 5, shallow turn position if operated by cornering mode switch 78, then turning switching control valve 72 is operated into by guide operating valve 73,74 and shallows turn position 72a.Thus, if deflecting bar 77 is operated into right 1st turning position R1, then right-hand corner control cock 67 is operated into supply position 67a, unloading valve 70 is operated into off-position 70a, working oil is supplied to the right engaging piece 33R of right side clutch 34() and right-hand corner power-transfer clutch 49, the right engaging piece 33R of right side clutch 34() be operating as dissengaged positions, right-hand corner power-transfer clutch 49 is operating as drive state.

In this case, as shown in Figures 2 and 3, turnon left power-transfer clutch 49 is half drive state, therefore the left engaging piece 33L of left side clutch 34() power, from left output gear 32L and turnon left power-transfer clutch 49(half drive state), via right-hand corner power-transfer clutch 49(drive state) be passed to right output gear 32R, identical with transmission shaft 29 rotation direction and be passed to right output gear 32R than the power of transmission shaft 29 slightly low speed.Thus, body changes direction to the right at leisure.

As shown in Figures 4 and 5, if deflecting bar 77 to be operated right 1st turning position R1, then right-hand corner control cock 67 is operated into supply position 67a as mentioned above, unloading valve 70 is operated into off-position 70a, simultaneously, working oil starts to shallow turn position 72a via proportional control valve 71 and turning switching control valve 72() and be supplied to and shallow turn power-transfer clutch 46, deflecting bar 77 more from right 1st turning position R1 to the right the 2nd turning position R2 operate, shallow turn the operation pressure of power-transfer clutch 46 more by proportional control valve 71 boost operations (as shown in Figure 6, solid line A1(with reference to the relation representing the operating position of deflecting bar 77 and the actuating current (shallowing turn the operation pressure of power-transfer clutch 46) of proportional control valve 71 shallows turn state)).

As shown in Figures 2 and 3, based on the operating position of deflecting bar 77, shallow turn the operation pressure of power-transfer clutch 46 by proportional control valve 71 boost operations, accompany with it, the power of transmission shaft 29 via right engaging piece 33R, transmission gear 45, shallow turn power-transfer clutch 46, transmission shaft 44, transmission gear 48, turning clutch case 47 and right-hand corner power-transfer clutch 49, identical with transmission shaft 29 rotation direction and than the transmission of power of transmission shaft 29 low speed to right output gear 32R.

In this case, as shown in Figures 2 and 3, become from left side clutch 34(left engaging piece 33L) power and be passed to the state of right output gear 32R from the power of shallowing turn power-transfer clutch 46 simultaneously, therefore in the scope (deflecting bar 77 is operated into the state of the vicinity of right 1st turning position R1) that the operation pressure of shallowing turn power-transfer clutch 46 is low pressure, from the left engaging piece 33L of left side clutch 34() power surpass power from shallowing turn power-transfer clutch 46, right output gear 32R is by from the left engaging piece 33L of left side clutch 34() power driven, body changes direction to the right at leisure.

Then, if deflecting bar 77 is operated right 2nd turning position R2 side by from right 1st turning position R1, the operation pressure of shallowing turn power-transfer clutch 46 is boosted a little, then as shown in Figures 2 and 3, surpass from the left engaging piece 33L of left side clutch 34(from the power of shallowing turn power-transfer clutch 46) power, right output gear 32R is by from the power driven of shallowing turn power-transfer clutch 46.In this condition, compared with right output gear 32R by from the left engaging piece 33L of left side clutch 34() power driven, at right output gear 32R by from the power operated situation of shallowing turn power-transfer clutch 46, right output gear 32R is driven with low speed, body is shallowed turn to the right, deflecting bar 77 is more operated by the 2nd turning position R2 side to the right, and the turn radius of body becomes less.

As shown in Figures 4 and 5, if deflecting bar 77 to be operated left 1st turning position L1, then turnon left control cock 68 is operated into supply position 68a, unloading valve 70 is operated into off-position 70a, working oil is supplied to the left engaging piece 33L of left side clutch 34() and turnon left power-transfer clutch 49, the left engaging piece 33L of left side clutch 34() be operating as dissengaged positions, turnon left power-transfer clutch 49 is operating as drive state.Meanwhile, carry out operation same as described above, body changes direction left at leisure.If deflecting bar 77 is operated left 2nd turning position L2 side from left 1st turning position L1, then carry out operation same as described above, body is shallowed turn left.

[9]

Then illustrate that the wheel one based on deflecting bar 77 stops one turn of pivot turn state.

As shown in Figures 4 and 5, if cornering mode switch 78 is operated wheel one to stop one turn of pivot turn position, then turning switching control valve 72 is operated into wheel one by guide operating valve 73,74 and stops one turn of pivot turn position 72b.Thus, if deflecting bar 77 to be operated right 1st turning position R1, then right-hand corner control cock 67 is operated into supply position 67a, unloading valve 70 is operated into off-position 70a, working oil is supplied to the right engaging piece 33R of right side clutch 34() and right-hand corner power-transfer clutch 49, the right engaging piece 33R of right side clutch 34() be operating as dissengaged positions, right-hand corner power-transfer clutch 49 is operating as drive state.In this case, turnon left power-transfer clutch 49 is half drive states, and therefore body changes direction to the right at leisure in the same manner as above-mentioned [8].

As shown in Figures 4 and 5, if deflecting bar 77 to be operated right 1st turning position R1, then described above, right-hand corner control cock 67 is operated into supply position 67a, and unloading valve 70 is operated into off-position 70a, simultaneously, working oil stops one turn of pivot turn position 72b via proportional control valve 71 and turning switching control valve 72(wheel one) start to be supplied to drg 50, deflecting bar 77 is more from right 1st turning position R1 the 2nd turning position R2 side operation to the right, the operation pressure of drg 50 more by proportional control valve 71 boost operations (as shown in Figure 6, solid line A2(wheel one with reference to the relation representing the operating position of deflecting bar 77 and the actuating current (operation pressure of drg 50) of proportional control valve 71 stops one turn of pivot turn state)).

As shown in Figures 2 and 3, based on the operating position of deflecting bar 77, the operation pressure of drg 50 is by proportional control valve 71 boost operations, accompany with it, braking force arrives right output gear 32R via transmission shaft 44, transmission gear 48, turning clutch case 47 and right-hand corner power-transfer clutch 49, makes braking force grow.

In this case, as shown in Figures 2 and 3, become from left side clutch 34(left engaging piece 33L) power and the braking force of drg 50 be passed to the state of right output gear 32R simultaneously, therefore in the scope (deflecting bar 77 is operated to the state of the vicinity of right 1st turning position R1) that the operation pressure of drg 50 is low pressure, from the left engaging piece 33L of left side clutch 34() power surpass the braking force of drg 50, right output gear 32R is by from the left engaging piece 33L of left side clutch 34() power driven.Thus, be that in the scope of low pressure, body changes direction to the right at leisure at the operation pressure of drg 50.

Then, if deflecting bar 77 is boosted a little from the operation pressure of right 1st turning position R1 the 2nd turning position R2 side operation, drg 50 to the right, then as shown in Figures 2 and 3, the braking force of drg 50 surpasses from the left engaging piece 33L of left side clutch 34() power, right output gear 32R utilizes the braking force of drg 50 to become braking mode, body to the right wheel one stops one turn of pivot turn, and deflecting bar 77 is the 2nd turning position R2 side operation more to the right, and the turn radius of body becomes less.

As shown in Figures 4 and 5, if deflecting bar 77 to be operated left 1st turning position L1, then turnon left control cock 68 is operated into supply position 68a, unloading valve 70 is operated into off-position 70a, working oil is supplied to the left engaging piece 33L of left side clutch 34() and turnon left power-transfer clutch 49, the left engaging piece 33L of left side clutch 34() be operating as dissengaged positions, turnon left power-transfer clutch 49 is operating as drive state.Meanwhile, carry out operation same as described above, body changes direction left at leisure.If deflecting bar 77 is operated left 2nd turning position L2 side from left 1st turning position L1, then carry out operation same as described above, body stops one turn of pivot turn to left wheel one.

As shown in Figures 4 and 5, the grip part of deflecting bar 77 has pole changer 77a.As described in above-mentioned [8], be operated at cornering mode switch 78 and shallow turn position, from right (left side) the 1st turning position R1(L1) (left side) the 2nd turning position R2(L2 to the right) operate the right side of deflecting bar 77 or a left side is shallowed turn state, produce with the needs of less semidiameter turn.

In this case, as shown in Figures 4 and 5, by deflecting bar 77 from right (left side) the 1st turning position R1(L1) (left side) the 2nd turning position R2(L2 to the right) the state that operates, if the pole changer 77a of pressing operation deflecting bar 77, then turning switching control valve 72 is operated into wheel one stops one turn of pivot turn position 72b from shallowing turn position 72a, and body to the right (left side) wheel one stops one turn of pivot turn.This wheel one stops one turn of pivot turn state only during the pole changer 77a of pressing operation deflecting bar 77, if hand takes away operation from the pole changer 77a of deflecting bar 77, then turning switching control valve 72 is stopped one turn of pivot turn position 72b from wheel one and is operated to and shallows turn position 72a, and body returns the state of shallowing turn.

[10]

Then, the wheel a positive and a negative pivot turn state based on deflecting bar 77 is described.

As shown in Figures 4 and 5, if cornering mode switch 78 is operated wheel a positive and a negative pivot turn position, then turning switching control valve 72 is operated to wheel a positive and a negative pivot turn position 72c by guide operating valve 73,74.Thus, if deflecting bar 77 to be operated right 1st turning position R1, then right-hand corner control cock 67 is operated into supply position 67a, unloading valve 70 is operated into off-position 70a, working oil is supplied to the right engaging piece 33R of right side clutch 34() and right-hand corner power-transfer clutch 49, the right engaging piece 33R of right side clutch 34() be operating as dissengaged positions, right-hand corner power-transfer clutch 49 is operating as drive state.In this case, turnon left power-transfer clutch 49 is half drive states, and therefore body changes direction to the right at leisure in the same manner as above-mentioned [8].

As shown in Figures 4 and 5, if deflecting bar 77 to be operated right 1st turning position R1, then described above, right-hand corner control cock 67 is operated into supply position 67a, and unloading valve 70 is operated into off-position 70a, simultaneously, working oil is via proportional control valve 71 and turning switching control valve 72(wheel a positive and a negative pivot turn position 72c) start to be supplied to reversing clutch 53, deflecting bar 77 more from right 1st turning position R1 to the right the 2nd turning position R2 operate, the operation pressure of reversing clutch 53 more by proportional control valve 71 boost operations (as shown in Figure 6, reference represents solid line A3(wheel a positive and a negative pivot turn of the relation of the operating position of deflecting bar 77 and the actuating current (operation pressure of reversing clutch 53) of proportional control valve 71)).

As shown in Figures 2 and 3, based on the operating position of deflecting bar 77, the operation pressure of reversing clutch 53 is by proportional control valve 71 boost operations, accompany with it, the power of transmission shaft 27 via transmission gear 51,52, reversing clutch 53, transmission shaft 44, transmission gear 48, turning clutch case 47 and right-hand corner power-transfer clutch 49, be passed to right output gear 32R as the power with transmission shaft 29 direction of rotation.

In this case, as shown in Figures 2 and 3, become from left side clutch 34(left engaging piece 33L) power and be passed to the state of right output gear 32R from the power of reversing clutch 53 simultaneously, therefore in the scope (deflecting bar 77 is operated to the state of the vicinity of right 1st turning position R1) that the operation pressure of reversing clutch 53 is low pressure, from the left engaging piece 33L of left side clutch 34() power surpass power from reversing clutch 53, right output gear 32R is by from the left engaging piece 33L of left side clutch 34() power driven.Thus, be that in the scope of low pressure, body changes direction to the right at leisure at the operation pressure of reversing clutch 53.

Then, deflecting bar 77 by from right 1st turning position R1 the 2nd turning position R2 side operation to the right, boosted a little at the operation pressure of reversing clutch 53 time, as shown in Figures 2 and 3, power from reversing clutch 53 surpasses from the left engaging piece 33L of left side clutch 34() power, right output gear 32R is by the power driven from reversing clutch 53.In this condition, right output gear 32R is driven to reversing sense relative to left output gear 32L, and body is the pivot turn of wheel a positive and a negative to the right, and deflecting bar 77 is the 2nd turning position R2 side operation more to the right, and the turn radius of body becomes less.

As shown in Figures 4 and 5, if deflecting bar 77 to be operated left 1st turning position L1, then turnon left control cock 68 is operated into supply position 68a, unloading valve 70 is operated into off-position 70a, working oil is supplied to the left engaging piece 33L of left side clutch 34() and turnon left power-transfer clutch 49, the left engaging piece 33L of left side clutch 34() be operating as dissengaged positions, turnon left power-transfer clutch 49 is operating as drive state.Meanwhile, carry out operation same as described above, body changes direction left at leisure.If deflecting bar 77 is operated left 2nd turning position L2 side from left 1st turning position L1, then carry out operation same as described above, body is to the positive one turn of pivot turn of left wheel one.

[11]

In above-mentioned [8], [9], [10] state is shallowed turn described in, wheel one stops in one turn of pivot turn state and wheel a positive and a negative pivot turn state, the relation of the operating position of deflecting bar 77 and the actuating current (shallowing turn the operation pressure of power-transfer clutch 46) of proportional control valve 71 is that the solid line A1(of Fig. 6 shallows turn state) represented by relation, the relation of the operating position of deflecting bar 77 and the actuating current (operation pressure of drg 50) of proportional control valve 71 is that the solid line A2(wheel one of Fig. 6 stops one turn of pivot turn state) represented by relation, the relation of the operating position of deflecting bar 77 and the actuating current (operation pressure of reversing clutch 53) of proportional control valve 71 is solid line A3(wheel a positive and a negative pivot turn states of Fig. 6) represented by relation.

Solid line A1(shallows turn state), A2(wheel one stops one turn of pivot turn state), A3(wheel a positive and a negative pivot turn state), become 2 curves that formula B1 shown below, B2, B3 are such.

B1(A1(shallows turn state)): Y1=a11XX-a21X+a31

B2(A2(wheel one stops one turn of pivot turn state)): Y2=a12XX-a22X+a32

B3(A3(wheel a positive and a negative pivot turn state)): Y3=a13XX-a23X+a33 wherein:

X: the operating position of deflecting bar 77

Y1: the actuating current (shallowing turn the operation pressure of power-transfer clutch 46) of proportional control valve 71

Y2: the actuating current (operation pressure of drg 50) of proportional control valve 71

Y3: the actuating current (operation pressure of reversing clutch 53) of proportional control valve 71

A11 ~ a33: positive constant

Thus, in the state of shallowing turn, wheel one stops in one turn of pivot turn state and wheel a positive and a negative pivot turn state, the unit operation electric current of the proportional control valve 71 corresponding with the unit operation amount of deflecting bar 77 is (by shallowing turn power-transfer clutch 46, drg 50 and reversing clutch 53 and unit velocity that right and left crawler travel device 1 occurs is poor) (unit velocity of the 1st and the 2nd state is poor), at the right side of deflecting bar 77 and left 1st turning position R1, the region of L1 side (N side, straight position) is medium and small, at the right side of deflecting bar 77 and left 1st turning position R2, large in the region of L2 side (steering lock side).

In this case, in positive constant a11 ~ a33, so-called

a11>a12>a13

a21>a22>a23

a31>a32>a33

Relation set up, as shown in Figure 6, formula B1(A1(shallows turn state)), formula B2(A2(wheel one stops one turn of pivot turn state)), formula B3(A3(wheel a positive and a negative pivot turn state)), be 2 times mutually different curves.Thus, stop in one turn of pivot turn state and wheel a positive and a negative pivot turn state at the state of shallowing turn, wheel one, turning performance each other not identical (being equivalent to the state making the variation characteristic of the unit velocity difference of the 1st state not identical with the variation characteristic of the unit velocity difference of the 2nd state).

Based on the relation of above-mentioned positive constant a11 ~ a33, as shown in Figure 6, in the region of the right side of deflecting bar 77 and left 1st turning position R1, L1 side (N side, straight position), the unit operation electric current that wheel one stops the proportional control valve 71 corresponding with the unit operation amount of deflecting bar 77 of unit operation current ratio wheel a positive and a negative pivot turn state of the proportional control valve 71 corresponding with the unit operation amount of deflecting bar 77 of one turn of pivot turn state is little.The unit operation electric current that the unit operation current ratio wheel one of shallowing turn the proportional control valve 71 corresponding with the unit operation amount of deflecting bar 77 of state stops the proportional control valve 71 corresponding with the unit operation amount of deflecting bar 77 of one turn of pivot turn state is little.

[the 1st other modes of the 1st embodiment]

Stop in one turn of pivot turn state and wheel a positive and a negative pivot turn state at the state of shallowing turn of above-mentioned [the 1st embodiment], wheel one, if any one establishment of state (1) (2) (3) shown below also can be configured to, then do not carry out the operation to high speed position (with reference to above-mentioned [5]) of the motor 11M of the hydrostatic continuously variable unit 11 of the varying speed switch 61a based on shifter bar 61.

(1) deflecting bar 77 to be operated between the right 1st and right 2nd turning position R1, R2 the state of (the left 1st and left 2nd turning position L1, L2 between).

(2) deflecting bar 77 to be operated between the right 1st and right 2nd turning position R1, R2 (the left 1st and left 2nd turning position L1, L2 between) and the gait of march of body is the state of the high speed of more than setting speed.

(3) deflecting bar 77 between the right 1st and right 2nd turning position R1, R2 midway location (the left 1st and left 2nd turning position L1, L2 between midway location) be operated to the state of right 2nd turning position R2 side (left 2nd turning position L2 side).

[the 2nd other modes of the 1st embodiment]

Stop in one turn of pivot turn state and wheel a positive and a negative pivot turn state at the state of shallowing turn of above-mentioned [the 1st embodiment], wheel one, if any one establishment of state (1) (2) (3) shown below also can be configured to, then do not carry out the operation to high speed position (with reference to above-mentioned [5]) of the motor 11M of the hydrostatic continuously variable unit 11 of the varying speed switch 61a based on shifter bar 61.

(1) by the action of shallowing turn power-transfer clutch 46, drg 50 and reversing clutch 53, the right side and left crawler travel device 1 produce the state of velocity contrast.

(2) by the action of shallowing turn power-transfer clutch 46, drg 50 and reversing clutch 53, right and left crawler travel device 1 produces velocity contrast and the gait of march of body is the state of the high speed of more than setting speed.

(3) by the action of shallowing turn power-transfer clutch 46, drg 50 and reversing clutch 53, right and left crawler travel device 1 produces velocity contrast and this velocity contrast state that to be setting speed difference above.

[the 3rd other modes of the 1st embodiment]

In above-mentioned [the 1st embodiment], [the 1st other modes of the 1st embodiment], [the 2nd other modes of the 1st embodiment], also can be configured to have without reversing clutch 53 shallow turn power-transfer clutch 46 and drg 50.If form in this wise, then shallowing turn power-transfer clutch 46 is the 1st turning mechanism, and drg 50 is the 2nd turning mechanism.

In above-mentioned [the 1st embodiment], [the 1st other modes of the 1st embodiment], [the 2nd other modes of the 1st embodiment], also can be configured to have without drg 50 shallow turn power-transfer clutch 46 and reversing clutch 53.If form in this wise, then shallowing turn power-transfer clutch 46 is the 1st turning mechanism, and reversing clutch 53 is the 2nd turning mechanism.

[the 4th other modes of the 1st embodiment]

In above-mentioned [the 1st embodiment], [the 1st other modes of the 1st embodiment] ~ [the 3rd other modes of the 1st embodiment], also can be configured to the characteristic (formula B2(A2(wheel one stops one turn of pivot turn state) that wheel one stops one turn of pivot turn state) with the characteristic (formula B3(A3(wheel a positive and a negative pivot turn state) of wheel a positive and a negative pivot turn state)) identical (in this case, as long as be set as a12=a13, a22=a23, a32=a33).

[the 5th other modes of the 1st embodiment]

In above-mentioned [the 1st embodiment], [the 1st other modes of the 1st embodiment] ~ [the 4th other modes of the 1st embodiment], also can be configured to formula B1(A1(and shallow turn state)), formula B2(A2(wheel one stops one turn of pivot turn state)), formula B3(A3(wheel a positive and a negative pivot turn state)) be not configured to 2 curves, the multiple straight lines (1 function) different by combination ramp rate and the characteristic that obtains as shown in Figure 6.

[the 2nd embodiment]

Then, with reference to Fig. 7 Figure 16, the 2nd embodiment is described.

In the 2nd embodiment, having the crawler belt stretch adjusting device of the laterally crawler travel device of the ground connection runner 124,125,126 of a side being rotatably arranged in track-frame 122, it is characterized by,

Have: guide member 152, the laterally side that the above-mentioned ground connection runner 124,125,126 being positioned at above-mentioned track-frame 122 is positioned at, supported by above-mentioned track-frame 122; Tensioning frame 151, is bearing on guide sections part 152 along track-frame fore-and-aft direction sliding freely; Tension wheel 127, be rotatably supported in mentioned strain adjustment framework 151 wheel body support 150 on and apply supporting role to crawler belt 129; Tension adjustment mechanism, relative to guide sections part 152 slide control mentioned strain adjustment framework 151,

For above-mentioned wheel body support 150, there is the form of bifurcation supporting above-mentioned tension wheel 127 on two horizontal sides.

As above-mentioned track takeup, such as, the device (with reference to paragraph [0019], Fig. 3) described in JP2005-335614A is had.

In the crawler belt stretch adjusting device described in the document, have: bracket, the rear end of track-frame can be inserted into slidingly back and forth; Straining pulley, pine turn is supported on the shaft on this bracket freely.

Straining pulley, by operating axis rotation and make bracket carry out screw thread feeding to move, thus carry out the tension adjustment of crawler belt.

In this crawler belt stretch adjusting device, have the fulcrum stretched out to a horizontal side from bracket, what make straining pulley be bearing in this fulcrum stretches out side, thus, the laterally side that the earthy runner making straining pulley be positioned at track bracket is positioned at, so that crawler belt is suitably wound on straining pulley.

In this crawler belt stretch adjusting device, if when turning etc. on crawler belt, there is high tension time, on the support unit of the fulcrum etc. of tension wheel, there is larger distortion, then there is the departing from mobile of tension wheel and crawler belt easily comes off.For this reason, tension wheel must be made to support securely, even if so that on crawler belt, occur that tension wheel also can not occur high tension depart from movement.In above-mentioned track tension control apparatus in the past, the fulcrum of tension wheel only tension wheel one-sided on supported, to make the supporting of tension wheel firm, then make the thicker grade of fulcrum and weight increased.

Correspondingly, formation according to the present embodiment, the guide member 152 of the laterally side adopting the ground connection runner 124,125,126 being positioned at track-frame 122 to be positioned at, thus the wheel body support 150 of tensioning frame 151 can be made to have the form of bifurcation supporting tension wheel 127 on two horizontal sides, and the laterally side that the ground connection runner 124,125,126 making straining pulley 127 be positioned at track bracket 122 is positioned at is so that crawler belt 129 can suitably be wound on straining pulley 127.Thus, the fulcrum of tension wheel 127 is supported in two horizontal sides of tension wheel 127, even if adopt the fulcrum, tensioning frame 151 etc. of tension wheel 127 small-sized than ever, even and if on crawler belt 129, there is high tension, tension wheel 127 also can be made to support securely and not depart from movement.

Therefore, make the supporting of tension wheel 127 firmly and not easily occur situation that crawler belt 129 comes off etc. and weight-saving crawler belt stretch adjusting device can be obtained from the viewpoint of tension wheel supporting construction.

Preferred guide sections part 152 is configured to, and more leaves from guide member 152 and adjust framework 151 for the state sliding guidance mentioned strain that track-frame 122 more rises with above-mentioned tension wheel 127.This is favourable in the following areas.

Observe the load based on crawler belt 129 of tension wheel 127, than tension wheel 127 be the tension force that occurs on the position in the direction of track-frame 122 closer to upside being positioned at of crawler belt 129 and being making a concerted effort of the tension force that the position in the direction tilted occurs relative to track-frame 122 closer to downside being positioned at than tension wheel 127, as crawler belt 129 tension force and apply to tension wheel.

If based on this formation, then the direction in the direction along tensioning frame 151 guided member 152 guiding movement to the direction of the load of tension wheel 127 applying due to the tension force of crawler belt 129, or the direction close with it, not easily twist between guide member 152 and tensioning frame 151, and can slide control tensioning frame 151.

Therefore, it is possible to obtain a kind of track tension control apparatus, this track tension control apparatus can make not easily to twist between guide member 152 and tensioning frame 151 and smooth and easy and carry out tension adjustment easily.

And then be configured on the side contrary with the side that above-mentioned track-frame 122 is positioned at relative to mentioned strain adjustment framework 151 by mentioned strain adjusting mechanism, and install along guide sections part 152 and mentioned strain adjustment framework 151, this is favourable in the following areas.

According to this formation, can not from relative to tensioning frame 151 side contrary with the side that track-frame 122 is positioned at be subject to based on track-frame 122 obstruction operate tension adjustment mechanism.

Therefore, it is possible to the operation of governing mechanism of tension 155 is carried out in the operation not being subject to track-frame 122 with hindering, thus acquisition can the smooth and easy crawler belt stretch adjusting device carrying out tension adjustment and operability excellence efficiently.

In addition, above-mentioned track-frame 122 is provided with guiding element installation portion 144, this guiding element installation portion 144 honours the crawler belt guiding element 143 that crawler belt 129 applies anticreep effect, on above-mentioned guiding element installation portion 144, possess the support 144a applying supporting role to above-mentioned tensioning frame 151, this is favourable in the following areas.

Guiding element installation portion 144 supports crawler belt guiding element 143, so have excellent intensity.Thus, according to the present invention, guiding element installation portion 144 can be used as supporting device and tensioning frame 151 is supported securely.

Therefore, it is possible to the simple structure by guiding element installation portion 144 being used as supporting device, obtain tensioning frame 151 can be carried out the tension adjustment of crawler belt 129 swimmingly track tension control apparatus by supporting securely.

Below, in further detail the 2nd embodiment is described.

Fig. 7 is the lateral plan of the working rig of the crawler belt stretch adjusting device A possessing present embodiment.As shown in the drawing, this Working mechanism becomes the crawler travel device 101,101 by pair of right and left and advances, and have: possess be equipped with drive attend a banquet 102 advance body and the portion that extracts 110 that links with the front portion of the organism frame 103 of this body of advancing of Drive Section, possess the sheller unit 104 and cereal box 105 that are arranged side by side along body transverse direction in the rear portion side of above-mentioned organism frame 103.

This working rig results rice or wheat etc.

Namely, extract portion 110, have to swing up and down with the front portion of above-mentioned organism frame 103 link freely extract framework 111, this extracts framework 111 by lifting pressure cylinder 112 by swinging operation up and down, thus lifting drops to the decline operating condition of Near Ground and above-mentioned point of careless part 113 the to raise rising non-operating condition of rising from ground for point careless part 113 be positioned at side by side along body transverse direction on the leading section in the portion of extracting 110.

When the body that makes making the portion that extracts 110 become decline state to advance is advanced, extract portion 110, by each point of careless part 113, import to the heaving mechanism 114 corresponding with along point careless part 113 in body transverse direction multiple heaving mechanisms 114 arranged side by side the upright paddy bar that extracts object and pull-up process is carried out to it, to by the upright paddy bar after each heaving mechanism 114 pull-up process, carry out extracting process by the extracting device 115 of hairclipper shape of, paddy bar is extracted to the top portion supply of the threshing conveyer chain 104a of threshing grain device 104 from what extract device 115 by feedway 116.

Sheller unit 104, transports to body rear to clamping the strain root side extracting paddy bar by threshing conveyer chain 104a, supplies this fringe point side extracting paddy bar and carry out threshing process to threshing chamber (not shown).Cereal box 105, reclaims and stores the threshing grain transported from sheller unit 104.

Fig. 8 is the lateral plan of the crawler travel device 101 in left side.Fig. 9 is the birds-eye view of the crawler travel device 101 in above-mentioned left side.The crawler travel device 101 on right side, has crawler travel device 101 same configuration with left side, eliminates the diagram of right side track moving device 101.As shown in these figures, crawler travel device 101 is configured to, and has: track-frame 122, links with above-mentioned organism frame 103 via the supporting arm 120,121 of above-mentioned a pair; Drive rotatable track sprocket 123, be bearing on above-mentioned organism frame 103 via change speed gear box (not shown) above the front of this track-frame 122; 8 pines turn ground connection runner 124,125,126 freely, and the horizontal side being positioned at body lateral outer side one side that advances of above-mentioned track-frame 122 is bearing on track-frame 122 along track-frame fore-and-aft direction side by side; Tension wheel 127, is arranged on the rearward end of track-frame 122 above the rear being arranged in the ground connection runner 126 near track-frame rear end side of above-mentioned 8 ground connection runners 124,125,126; The pine that front and back are a pair turns carrying roller 128,128 freely, be bearing on above-mentioned organism frame 103 above above-mentioned track-frame 122, and have along above-mentioned track sprocket 123, above-mentioned 8 ground connection runners 124,125,126, above-mentioned tension wheel 127, the carrying roller 128,128 of above-mentioned front and back a pair and the rubber of winding crawler belt 129.

The supporting arm 120 of above-mentioned front side, via by the base portion of this supporting arm 120 and the rotation fulcrum 120a that organism frame 103 rotatably links and the coupled arm 130 that arranges rotatably integrally on the end of the side contrary with the side that above-mentioned supporting arm 120 links of this rotation fulcrum 120a, with the pressure cylinder bar 131a interlock of hydraulic actuating cylinder 131.

That is, the supporting arm 120 of front side, utilize above-mentioned hydraulic actuating cylinder 131 and around the axle core of above-mentioned rotation fulcrum 120a relative to organism frame 103 by swinging operation up and down, and relative to the front of organism frame 103 descending operation track-frame 122.

The supporting arm 121 of above-mentioned rear side, via by the base portion of this supporting arm 121 and the rotation fulcrum 121a that organism frame 103 rotatably links and the coupled arm 132 that arranges rotatably integrally on the end of the side contrary with the side that above-mentioned supporting arm 121 links of this rotation fulcrum 121a, with the pressure cylinder bar 133a interlock of hydraulic actuating cylinder 133.The free end side of the supporting arm 121 of rear side, links with the rear end side of track-frame 122 via payment connecting rod 134.

Namely, the supporting arm 121 of rear side, utilize above-mentioned hydraulic actuating cylinder 133 and around the axle core of above-mentioned rotation fulcrum 121a relative to organism frame 103 by swinging operation up and down, via payment connecting rod 134 by the rear end side of track-frame 122 relative to organism frame 103 descending operation.

That is, the supporting arm 120,121 of the front and back a pair of the crawler travel device 101,101 of left and right is by swinging operation, thus body of advancing tilts to transverse direction or fore-and-aft direction relative to ground.

Namely, carry out swinging operation, to rise together or decline swing with the supporting arm 120,121 of the front and back a pair making a side of the crawler travel device 101 of left and right, and the rising of the supporting arm 120,121 of front and back a pair or descending stroke identical, thus make the track-frame 122 of a side of the crawler travel device 101 of left and right rise abreast relative to organism frame 103 or decline, the end side of advancing in the transverse direction of body using the earth point of the crawler travel device 101 of another side as swing pivot, and relative to ground rise or fall.

Carry out swinging operation, rise with a side of the supporting arm 120 of front side and the supporting arm 121 of rear side that make the crawler travel device 101 of left and right or decline and swing, and the supporting arm 120 of the crawler travel device 101 of left and right, rising or the descending stroke of 121 are identical, thus the track-frame 122 of the crawler travel device 101 of left and right swings using the earth point of front as swing pivot up and down relative to organism frame 103, or swing up and down using the earth point of rear end side as swing pivot relative to organism frame 103, advance wherein one end of fore-and-aft direction of body using the other end as swing pivot relative to ground rise or fall.

Then, the ground connection runner 126 near track-frame rear end side of the ground connection runner 124,125,126 being arranged in above-mentioned 8 is called last ground connection runner 126, the ground connection runner 125 of position that is forward for the above-mentioned last ground connection runner 126 of the ground connection runner 124,125,126 be arranged in than above-mentioned 8, that close with last ground connection runner 126 neighbour is called rear ground connection runner 125 and is described.

Above-mentioned rear ground connection runner 125 and above-mentioned last ground connection runner 126, only pine turn is bearing on track-frame 122 freely, makes it can not be elevated relative to track-frame 122.

The ground connection runner 124 of the above-mentioned last ground connection runner 126 of the removing in above-mentioned 8 ground connection runners 124,125,126 and above-mentioned rear ground connection runner 125, two the ground connection runners 124,124 neighbour closed divide into groups and are formed as a runner group, and two ground connection runners of each runner group 124,124 are concentrated and with the state lower support linked by a cantilever connecting member 140 and track-frame 122 on track-frame 122.

As shown in Figure 9, Figure 10, above-mentioned each cantilever connecting member 140, is rotatably bearing on track-frame 122 via the adapter shaft 141 being positioned at intermediate portion.Form the ground connection runner 124 of a side of two ground connection runners 124,124 of each runner group, pine turn is bearing in the above-mentioned adapter shaft 141 of ratio of above-mentioned cantilever connecting member 140 freely closer on the position of front, the ground connection runner 124 of the opposing party, pine turn is bearing in the above-mentioned adapter shaft 141 of ratio of above-mentioned cantilever connecting member 140 freely closer on the position of rear end side.

Thus, the ground connection runner 124 of the above-mentioned last ground connection runner 126 of the removing in 8 ground connection runners 124,125,126 and above-mentioned rear ground connection runner 125, form two ground connection runners 124,124 of above-mentioned each runner group, be arranged on track-frame 122 by cantilever connecting member 140, by the swing of cantilever connecting member 140, be reciprocally elevated relative to track-frame 122 using the axle core of above-mentioned adapter shaft 141 as swing pivot.

Crawler travel device 101, has: crawler belt guiding element 142, arranges corresponding to above-mentioned each runner group; Crawler belt guiding element 143, is arranged corresponding to above-mentioned rear ground connection runner 125 and above-mentioned last ground connection runner 126.

As shown in Fig. 8, Figure 10, above-mentioned crawler belt guiding element 142 corresponding to above-mentioned each runner group is configured to be had: bar-shaped guiding element body 142a, to the guide wheel body of the pair of right and left of the ground connection runner 124 of the opposing party between the guide wheel body of the pair of right and left of the ground connection runner 124 of the side from runner group; Pipe link 142b, links this guiding element body 142a and above-mentioned cantilever connecting member 140, and by guiding element body 142a, the axle to the left and right of crawler belt 129 raised 129a, 129a apply locking effect and carry out the anticreep of crawler belt 129.Corresponding to the crawler belt guiding element 142 of each runner group, by by above-mentioned guiding element body 142a and above-mentioned pipe link 142b integrally casting and making together with above-mentioned cantilever connecting member 140.

As shown in Figure 10, above-mentioned crawler belt guiding element 143 corresponding to above-mentioned last ground connection runner 126 and above-mentioned rear ground connection runner 125 is configured to be had: bar-shaped guiding element body 143a, to the guide wheel body of the pair of right and left of last ground connection runner 126 between the guide wheel body of the pair of right and left from rear ground connection runner 125; Pipe link 143b, links the guiding element installation portion 144 that this guiding element body 143a and track-frame 122 possess, and by guiding element body 143a, the raised 129a of the axle to the left and right of crawler belt 129 applies locking effect and carries out the anticreep of crawler belt 129.This crawler belt guiding element 143, is made by integrally casting above-mentioned guiding element body 143a and above-mentioned pipe link 143b.

The above-mentioned guiding element installation portion 144 of track-frame 122, the transverse side of track-frame 122 sets up derby and forms.This guiding element installation portion 144, the end of guiding element installation portion 144 is provided with three binder bolts 145 side by side along the above-below direction of track-frame 122 and fore-and-aft direction triangle configuration ground, thus supports the union lever 143b of above-mentioned crawler belt guiding element 143.

Crawler travel device 101, has the crawler belt stretch adjusting device A of the present embodiment on the rear portion being arranged on track-frame 122.

Fig. 9 represents the structure overlooked of the crawler belt stretch adjusting device A of present embodiment.Figure 10 represents the structure of the side-looking of the crawler belt stretch adjusting device A of present embodiment.Figure 11 is the vertical profile birds-eye view of the crawler belt stretch adjusting device A of present embodiment.Figure 12 is the longitudinal cross-sectional side view of the crawler belt stretch adjusting device A of present embodiment.As shown in these figures, the crawler belt stretch adjusting device A of present embodiment is configured to have: above-mentioned tension wheel 127; Tensioning adjustment framework 151, is turned by wheel body support 150 pine and supports this tension wheel 127 freely; Guide member 152, supports this tensioning frame 151; Tension adjustment axle 155, the fastener 153a from the horizontal sidepiece being darted at above-mentioned wheel body support 150 is until the support 154 that is arranged on guide sections part 152 and installing.

Mentioned strain adjustment framework 151 is configured to, and except possessing above-mentioned wheel body support 150, also possess frame body 151a, the angle-steel tubing that this frame body 151a is linked by the base portion of end side and this wheel body support 150 is formed.

Figure 15 is the birds-eye view of above-mentioned wheel body support 150.Figure 16 is the lateral plan of above-mentioned wheel body support 150.As shown in these figures, the axle that above-mentioned wheel body support 150 has form of bifurcation props up wheel fork 156, and this axle props up wheel fork 156 has a pair axle with the configuration on be positioned at tension wheel 127 discretely two horizontal sides and props up hole 156a, 156a.As shown in figure 11, wheel body support 150, props up wheel fork 156 by above-mentioned axle, at the fulcrum 127a of two horizontal side bearing tension wheels 127 of tension wheel 127.That is, at two horizontal side bearing tension wheels 127.

Guide sections part 152, be configured in a laterally side identical with the laterally side that above-mentioned each ground connection runner 124,125,126 is positioned at of track-frame 122, be bearing on supporting arm 122a, 122a of the front and back a pair of track-frame 122, tensioning frame 151 is configured on the suitable position of a laterally side of track-frame 122, the position of the crawler belt 129 that namely suitably can reel on tension wheel 127.

As shown in Figure 12 ~ Figure 14, the mentioned strain adjustment framework 151 of guide sections part 152 the end of side of give prominence to and mentioned strain adjust framework 151, be mounted in the link 157 on the support 144a be made up of the upper surface of the above-mentioned installation portion 144 of track-frame 122 via bottom, by above-mentioned support 144a from below stop support.Above-mentioned link 157 is made up of upside sheet metal member 157a and downside sheet metal member 157b, the side of described upside sheet metal member 157a applies stopping function towards the lower surface of guide member 152 and tensioning frame 151, and described downside sheet metal member 157b to be clipped on the upside of this between sheet metal member 157a and above-mentioned support 144a.

Mentioned strain adjustment framework 151, its frame body 151a is embedded in guide sections part 152 sliding freely, thus guided member 152 supports sliding freely, the medial surface sliding guidance of the guided member 152 and fore-and-aft direction along track-frame 122 slides.Tensioning frame 151, direction of slip is arranged according to the installation direction of guide member 157, thus tension wheel 127 slides more to leave from guide member 152 state more risen relative to track-frame 122.Namely, tensioning frame 151, by crawler belt 129 to be positioned at than tension wheel 127 be the tension force at the position in direction along track-frame 122 closer to upside and be positioned at than tension wheel 127 tension force at the position closer to downside for track-frame 122 being the direction tilted, slide along the direction close with the direction of the load applied to tension wheel 127.

Mentioned strain adjustment axle 155, be made up of threaded shaft, this threaded shaft is screwed with the negative thread of the adjustment axle inserting hole arranged on the above-mentioned support 154 of guide member 152, during rotary manipulation, to move and above-mentioned fastener 153a to wheel body support 150 applies by or draws effect along track-frame fore-and-aft direction relative to guide member 152, thus, relative to guide member 152 slide control Tensioning frame 151.This tension adjustment axle 155, is configured on the side contrary with the side that track-frame 122 is positioned at relative to tensioning frame 151, can not by operating based on the operating barrier of track-frame 122 outside the body horizontal stroke of advancing of crawler travel device 101.

Generally speaking, crawler belt stretch adjusting device A, by rotary manipulation tension adjustment axle 155, makes tensioning frame 151 mobile adjustment by guide member 152 and link 157 sliding guidance by this tension adjustment axle 155.Now, tensioning frame 151, by crawler belt 129 tension force and slide along the direction close with the direction of the load applied to tension wheel 127, with not easily between tensioning frame 151 and guide member 152 produce reverse slide in state dynamic.So, tension wheel 127 moved to its side, rear relative to track-frame 122 regulate and to closer to moving device rear side pressing crawler belt 129, thus to increase side adjustment crawler belt 129 tensile force.Or, tension wheel 127 relative to track-frame 122 forwards side be moved regulate and the pressing of crawler belt 129 is weakened, thus, to reduce side adjustment crawler belt 129 tensile force.

As shown in Figure 15, Figure 16, above-mentioned wheel body support 150, propping up wheel fork 156 and above-mentioned fastener 153a except possessing above-mentioned axle, also possessing: the strengthening rib 158,158 of upper and lower a pair, being arranged on axle and propping up on the outer circumferential side of wheel fork 156; 2nd fastener 153b, props up wheel fork 156 relative to above-mentioned axle and is arranged on the side contrary with the side that above-mentioned fastener 153a is positioned at.Above-mentioned axle props up wheel fork 156 and above-mentioned fastener 153a and above-mentioned strengthening rib 158 and above-mentioned 2nd fastener 153b, by investment casting casting by integrally casting.

Above-mentioned 2nd fastener 153b, time on the crawler belt stretch adjusting device A of crawler travel device 101 tensioning frame 151 being equipped in right side, installation tension adjustment axle 155.

[other embodiments of the 2nd embodiment]

Also can replace above-mentioned embodiment, adopt the formation by grease pressure cylinder slide control tensioning frame 151, also can realize object of the present invention.Therefore, tension adjustment axle 155, grease pressure cylinder etc. are generically and collectively referred to as tension adjustment mechanism.

[the 3rd embodiment]

Then, with reference to Figure 17 ~ Figure 35, the 3rd embodiment is described.

In the 3rd embodiment; for a kind of grain recoverer of combination machine drives structure; ground, left and right configuration sheller unit 207 and cereal box 208 side by side; and on the front side of cereal box 208, be laterally configured with driving engine 204; leading section to the end screw rod 210 of above-mentioned cereal box 208 transmits engine power; it is characterized by

Output shaft 263 is projected to body to horizontal foreign side from above-mentioned driving engine 204, and laterally support has tween drive spindle 271 in the front side of above-mentioned cereal box 208, interlock links body inside line and the above-mentioned output shaft 263 of above-mentioned tween drive spindle 271, and interlock links the body outside left of above-mentioned tween drive spindle 271 and the leading section of end screw rod 210.

Grain recoverer as sheller unit drives structure; be known to following formation (such as with reference to JP9-205867A); the body inward side position that interlock links the tween drive spindle of the output shaft projected in body from the driving engine laterally configured and the front side being laterally provided in cereal box is wrapping with via driving band; and the body inward side position that interlock links tween drive spindle and the input magazine be equipped with on the front portion of cereal box, be passed to the leading section of end screw rod by engine power via tween drive spindle and input magazine.

In above-mentioned structure in the past, the output shaft projected from driving engine is positioned at the position away from body side compared with the end screw rod of cereal box, so driving engine to be arranged in order to the left and right weight balancing of body in body side, then bear about the tween drive spindle of engine power longer.

Particularly, be configured to the longitudinal fulcrum of cereal box around rear portion is rotated to body foreign side, thus open the horizontal sidepiece of sheller unit significantly, and, the input part of the outer square end of the body forming tween drive spindle discretely and cereal box can be connected, automatically be separated from tween drive spindle with the input part of the open interlock of the rotation of cereal box and cereal box, interlock is rotated and the input part of cereal box is automatically connected with tween drive spindle with the recovery of cereal box, in such formation, the pars intermedia that parts support tween drive spindle accurately must be propped up by other axle, so that the intermediate transmission shaft position staying the length of body side when the rotation of cereal box is open does not change, the number of components forming drive structure increases, and cost up.

On the other hand, if formation according to the present embodiment, even if then driving engine 204 is configured in side in body, output shaft 263 also from driving engine 204 to body horizontal foreign side outstanding, therefore, crossbearer can be made close along body transverse direction in the interlock position of the leading section of the body inside line of the tween drive spindle 271 of the front side of cereal box 208 and the body outside left of tween drive spindle 271 and end screw rod 210, and tween drive spindle 271 shortens.Short tween drive spindle 271, the demand carrying out therebetween supporting reduces.

Therefore, driving engine 204 to be arranged in body side and the left and right weight balancing of body can be made suitable, and the miniaturization and simple and easy in the transverse direction of the drive structure of the end screw rod 210 from driving engine 204 to cereal box 208 can be made.

Preferably above-mentioned cereal box 208 is configured to rotate around longitudinal fulcrum P at rear, and the front portion of input magazine 251 with above-mentioned cereal box 208 is linked, with wick-like ground above-mentioned input magazine 251 arranged opposite possess to the input shaft 254 in body and above-mentioned tween drive spindle 271, possess at its opposed position from the de-power-transfer clutch 273 of shaft core direction card.This formation is favourable in the following areas.

If according to above-mentioned formation, then pass through cereal box 208 to sideway swivel outside body, can automatically disconnect the interlock of tween drive spindle 271 and end screw rod 210 and leave from sheller unit 207 significantly, easily can carry out the maintenance of the sidepiece of sheller unit 207 from open space.Tween drive spindle 271 accept outstanding inside body from input magazine 251 from the input shaft 254 of the power of tween drive spindle 271, so correspondingly can be made shorter.

Below, the 3rd embodiment is illustrated in greater detail.

Figure 17, represents the lateral plan seen on the right side of body of head feeding type combined harvester (wholeculmdischargingtypecombine-harvester).This combination machine is configured to, the portion that extracts 203 of multiple strip harvesting part specification lifting freely links with the front portion of organism frame 202 of the crawler travel device 201 possessing pair of right and left, the right front of above-mentioned organism frame 202 is equipped with the former dynamic portion 205 built with driving engine 204 and Drive Section 206, and, sheller unit 207 is equipped with in the left side of organism frame 202, and on the position of the rear side in former dynamic portion 205, the cereal box 208 of sheet metal structure is equipped with on the right side of sheller unit 207, be supplied to sheller unit 207 by by extracting the paddy bar that portion 203 extracts and carry out threshing process, the device 209 of winnowing of screw is raised to send and is sorted the grain of recovery by sheller unit 207 and be fed into cereal box 208.

As shown in Figure 20 and Figure 24, above-mentioned cereal box 208, sees at fore-and-aft direction, narrow shape under being formed as its underpart, and, in the right lateral surface of side in body, be formed with the lengthwise recess 208a entering and configure above-mentioned device 209 of winnowing.Be formed with recess 208b, 208c in the front and back of above-mentioned lengthwise recess 208a, this recess 208b, 208c avoid the interference at the device position outstanding with the right flank to sheller unit 207, are formed with the bulge 208d of increment at the front upper of lengthwise recess 208a.Thus, make the right side shape of the left-hand face of cereal box 208 and sheller unit 207 as far as possible close, thus large container capacity can be guaranteed.

In the lower end of the lower narrow portion 208e of above-mentioned cereal box 208, via fulcrum 210a, anterior-posterior horizontal floor-engaging frame has the end screw rod 210 rearward sending the grain stored, and along the top of end screw rod 210, via rotating fulcrum 212 can swingingly support have cross sectional shape to be formed as chevron flow down directing plate 211.

The lower narrow portion 208e of cereal box 208, be applied in the angle of inclination flowing down more than loll of grain, so that the grain stored is not residual and be directed into end screw rod 210, and, configure the bottom of lower narrow portion 208a significantly to horizontal foreign side from the center of container width, more more outward than organism frame 202 to make screw rod of the above-mentioned end 210 be positioned at.Make the lower end part of the lower narrow portion 208e of screw rod 210 at the bottom of collecting in than organism frame 202 more lateral in this wise, compared with situation in the top of organism frame 202 of the lower end part of the lower narrow portion 208e of cereal box 208, the bottom of the lower narrow portion 208e of cereal box 208 can be set lowlyer, thus, container upper end position can not be made to improve and increase container height (lower-upper length), thus can capacity increasing.

The threshing grain being equipped with screw at the rear of cereal box 208 transports device 213, and this threshing grain transports after the grain sent by end screw rod 210 raises and send by device 213, horizontal transport and transporting outside machine.This threshing transports device 213, the vertical conveyer 213A with the screw be connected with the lower end below of the cereal box 208 and horizontal conveyer 213B of screw be connected with the upper end of this vertical conveyer 213A, grain transports the entirety of device 213, can by the screw rod axle center with vertical conveyer 213A with in rotary moving centered by longitudinal fulcrum P of core.

As shown in figure 22, what be linked with the rearward end of the fulcrum 210a of supporting end screw rod 210 in the rear end, bottom of above-mentioned cereal box 208 transports case 214, and the above-mentioned lower end boss portion 214a transporting case 214 can be fitted together to rotationally and be bearing in the support 202a outstanding to body foreign side from organism frame 202, and cereal box 208 can be supported rotatably around above-mentioned longitudinal fulcrum P.As shown in figure 28, the bottom front surface of cereal box 208 has the back plate 215 be made up of heavy-gauge sheeting, the bottom mounting of this back plate 215 is bearing on the upper surface of organism frame 202, and the total weight of cereal box 208 is supported by organism frame 202 and support 202a in former and later two positions.

Above-mentioned back plate 215 can slide up and down to possess lock pin 220.Lock pin 220 is exerted a force by slip downwards by spring 221; by being arranged on the bottom of inserting lock pin 220 in the locking hole 222 on organism frame 202 side; cereal box 208 can be fixed on set threshing and reclaim position; extracting lock pin 220 by overcoming spring 221 from locking hole 222, cereal box 208 can be made around the in rotary moving and maintenance position that the is right side of open sheller unit 207 significantly of longitudinal fulcrum P.In addition, above-mentioned lock pin 220, can engage on the metal bracket 223 remaining on and back plate 215 possesses by above pulling out rotation.

As shown in Figure 17 ~ Figure 19, Figure 27, the lateral outer side of cereal box 208 links the side cover 225 being fixed with covering container side surface.On the bottom of side cover 225, be linked with the lower side cover 226 of the outside lower narrow portion 208e covering cereal box 208 from horizontal foreign side.In the rearward end of side cover 225, be linked with rear portion side cover 227, this rear portion side cover 227 covers from horizontal side the major part that grain transports the vertical conveyer 213A of device 213, and possesses working lamp 228 and overall width lamp 229 etc.In the rearward position of vertical conveyer 213A, erect the vertical framework 231 of cornue from organism frame 202, the back cover 230 covering vertical conveyer 213A from rear links fixing with this vertical framework 231.When cereal box 208 rotates to horizontal foreign side around longitudinal fulcrum P, as shown in the imaginary line in Figure 19, the rear portion side cover 227 in rotary moving integratedly with cereal box 208 does not produce with fixing back cover 230 interferes and proceeds to rear.As shown in figure 28, on the leading section of lower side cover 226, can swing around longitudinal fulcrum a and openedly and closedly be provided with movable hood 232, by opening this movable hood 232, above-mentioned lock pin 220 exposes, and locking operation and the locking that can carry out cereal box 208 remove operation.

Above-mentioned grain transports the vertical conveyer 213A of device 213, forms in the tote box 235 being contained in the longitudinal direction be made up of circular pipe in vertical feed screw 236.As shown in figure 22, the bottom of tote box 235 can around longitudinal fulcrum P rotationally by slotting embedding supporting relative to the above-mentioned case 214 that transports, and, by on two positions up and down of above-mentioned vertical framework 231 the tubular support unit 237 that possesses can support rotationally, keep the posture of standing up of vertical conveyer 213A.The lower end of the fulcrum 236a of vertical feed screw 236 is inserted into above-mentioned transporting in case 214, and the rearward end finishing bevel gear cuter interlock of fulcrum 210a with screw rod of the above-mentioned end 210, indulge feed screw 236 with the speed drive identical with end screw rod 210.

As shown in Figure 22 and Figure 26, in the above-mentioned bottom transporting case 214, be formed with access R, the grain sent by end screw rod 210 is directed into the transport zone of the vertical feed screw 236 of vertical conveyer 213A by this access R, this access R, the shape transporting mouthful 208f of the lower shape and cereal box 208 that transport case 214 is formed as the Long Circle of lengthwise respectively, to become the elongate shape expanded upward from the upper end of end screw rod 210.

As shown in figure 23, above-mentioned grain transports the horizontal conveyer 213B of device 213, by being inserted in the infeed screw rod 239 of the fulcrum 239a in the large footpath of fulcrum 236a possessed than above-mentioned vertical fortune screw rod 236 by forming in the tote box 238 formed with the circular pipe in footpath with the tote box 235 of vertical conveyer 213A, the top ends of tote box 238 possesses the discharge orifice 240 of opening in downward direction.The vertical upper end of tote box 235 of conveyer 213A and the base end part of the tote box 238 of horizontal transveyer 213B, the connection that is connected by connecting box 241.The cardinal extremity connecting box portion 241b that connecting box 241 comprises the upper end connecting box portion 241a on the upper end of the tote box 235 being packed in vertical conveyer 213A and is packed on the base end part of the tote box 238 in horizontal conveyer 213B, cardinal extremity connecting box portion 214b can around horizontal fulcrum Q chimeric link rotationally relative to connecting box portion, upper end 241a, and horizontal conveyer 213B can swing up and down around above-mentioned horizontal fulcrum Q.

The relay axis 242 of two supports on above-mentioned upper end in succession case portion 241a and cardinal extremity connecting box portion 241b be equipped with on above-mentioned horizontal fulcrum Q.This relay axis 242 is equipped with the feeding impeller 243 tilted relative to horizontal fulcrum Q, and the two ends of relay axis 242 respectively with the cardinal extremity of the upper end of the fulcrum 236a of vertical feed screw 236 and the fulcrum 239a of infeed screw rod 239 with constant speed finishing bevel gear cuter interlock.Thus, synchronously driven with the rotation interlock of end screw rod 210 and vertical feed screw 236 and infeed screw rod 239, the grain sent from cereal box 208 is indulged after conveyer 213A raises and send, and is discharged from discharge orifice 240 by the horizontal transport of horizontal conveyer 213B.

The relay axis of above-mentioned case in succession 241 inserts position, be formed as footpath larger than the tote box 238 of the tote box 235 of vertical conveyer 213A and horizontal conveyer 213B, the sectional area of grain path of the sectional area of deduction relay axis 242 is set as the sectional area of the grain path after than the deduction fulcrum sectional area of vertical conveyer 213A and larger than the sectional area of the grain path of the deduction fulcrum sectional area of horizontal conveyer 213B, make to improve relative to the degree of freedom of the grain movement of case 241 in succession, make do not block to the handing-over of the grain of horizontal conveyer 213B from Zong Yunyun mechanism 213A and carry out swimmingly.From the upper end be fixed on above-mentioned vertical conveyer 213A in succession case portion 241a until horizontal conveyer 213B tote box 238 and set up hydraulic actuating cylinder 245, by the expanding-contracting action of this hydraulic actuating cylinder 245, horizontal conveyer 213B is driven swing around above-mentioned transverse axis heart Q up and down in given area.

As shown in figure 25, being fixed on the above-mentioned of the bottom of cereal box 208 in link transports on case 214, the electro-motor 246 of band reductor is installed, and, slowed down by it and export and the miniature gears 247 of positive and negative ground rotary actuation, engage with flange shape the Internal gear 248 be packed on the tote box 235 of vertical conveyer 213A, by the rotating action of electro-motor 246, grain transports device 213 entirety and is driven in rotation around longitudinal fulcrum P.Utilize grain to transport the rotation of device 213 and swinging up and down of horizontal conveyer 213B in this wise, the position of rotation of discharge orifice 240 and height and position are moved, can at random change grain drain position.

Then, the drive structure to transporting the screw rod of the above-mentioned end 210 of the power shaft of device 213 as the above-mentioned grain of driving is described.

As shown in Figure 29 ~ Figure 32, on the above-mentioned back plate 215 that the front lower of cereal box 208 possesses, be fixed with the bracket 250 of the leading section of the fulcrum 210a of bearing supporting end screw rod 210, the front surface of this bracket 250 links input magazine 251.In input magazine 251, be equipped with the input finishing bevel gear cuter 252 linked with above-mentioned fulcrum 210a and the input finishing bevel gear cuter 253 engaged with it, the input shaft 254 linked with input finishing bevel gear cuter 253 side in body projects.

Above-mentioned bracket 250 and input magazine 251, make the involutory link of bight 250a, 251a, and in the space formed between bight 250a, 251a, the core shift cam 256 being provided with bearing 255 in periphery is fixed on the fulcrum 210a of end screw rod 210 by outer.The above-mentioned rotating fulcrum 212 flowing down directing plate 211 is outstanding to the front of back plate 215, and the motion arm 257 linked with its jag engages with the bearing 255 of above-mentioned core shift cam 256 via upper and lower elongated hole 258.According to this formation, the fulcrum 210a of end screw rod 210 is driven in rotation and core shift cam 256 rotates, the motion arm 257 engaged with this core shift cam 256 is reciprocally swinging with the amplitude of the core shift amount corresponding to core shift cam 256, flow down directing plate 211 to be driven by reciprocally swinging in first retainer, thus arch formation can not occur the grain stored in container and sphere of action to end screw rod 210 flows down.

On organism frame 202 between cereal box 208 and the above-mentioned driving engine 204 being configured in its front, be equipped with bearing bracket 260, engine power is passed to the input belt wheel 261 rotatably installing the horizontal axle center be bearing on this bearing bracket 260.

As shown in the diagram of gears of Figure 21, in the above-mentioned driving engine 204 laterally carrying outfit, to possess in body the output shaft 263 of the outstanding main output shaft 262 in side and the slave outstanding to body foreign side driving, crawler travel device 201, extract portion 203 and sheller unit 207 by the power driven obtained from main output shaft 262.Outside output shaft 263 possesses the output pulley 264 of 3, the driving band 265 that the water pump 266 of radiator cooling, cooling fan of engine 267, electrical generator 268 are wound onto on this output pulley 264 drives, and the other driving band 269 be wound on above-mentioned output pulley 264 is wound onto on above-mentioned input belt wheel 261.In addition, although not shown, above-mentioned output pulley 264 can also reel other driving band, can drive the compressor that the cooling media of the interior environment system in the machine being equipped in passenger cabin specification compresses.

As described above, tween drive spindle 271 can along axis direction slidably spline be embedded in the center of the above-mentioned input belt wheel 261 bearing engine power.Tween drive spindle 271, with the above-mentioned input shaft 254 of support on above-mentioned input magazine 251 with the core involutory configuration in ground, and tween drive spindle 271 is subject to input shaft 254 force of sliding by the spring 272 of outer installation.Tween drive spindle 271 and input shaft 254, at its involutory opposed position, via engagement type power-transfer clutch 273, interlock links.

Above-mentioned power-transfer clutch 273, comprise the clutch components 274 that links and be fixed on the boss-shaped of the top ends of tween drive spindle 271 and by the engaging part 275 squeezed into through spring pin form on the top ends periphery of input shaft 254, in the top ends of clutch components 274 fitted in input shaft 254, thus as shown in figure 29, engaging part 275 engagement of input shaft 254 snaps in the engaging recessed part 276 on the end diagonal position being formed in clutch components 274, thus, the transmission of power from tween drive spindle 271 to input shaft 254 is carried out.

If cereal box 208 is in rotary moving to maintenance position from grain recovery position, then as shown in figure 30, accompany with the movement to horizontal foreign side of input shaft 254, engaging part 275 is extracted from clutch components 274, removes the link of tween drive spindle 271 and input shaft 254.Contrary; if cereal box 208 reclaims position from maintenance position to original grain, rotation returns; then accompany with the movement of side in transverse direction of input shaft 254, engaging part 275 engages from axis direction with clutch components 274, and tween drive spindle 271 and input shaft 254 automatically interlock link.Cereal box 208 reclaims position and rotates when returning from maintenance position to grain; the rotatable phase of the engaging recessed part 276 of the clutch components 274 stopped the rotation and the engaging part 275 of input shaft 254 offsets sometimes; in this case; engaging part 275 abuts the external end edge of pressing clutch components 274, and tween drive spindle 271 overcomes spring 272 and square retrogressing of sliding in body.Then, start the engine 204 and middle S. A. 271 start to rotate, when then the engaging recessed part 276 of clutch components 274 moves to the phase place of engaging part 275, middle S. A. 271 force is slided and power-transfer clutch 273 is connected, and makes middle S. A. 271 and input shaft 254 automatically become the state of interlock link.

As shown in Figure 33 ~ Figure 35, about the direction A/F w of above-mentioned engaging recessed part 276 is set to the several times of the external diameter of engaging part 275, and the degree of depth d of engaging recessed part 276 is set to slightly larger than the external diameter of engaging part 275, and and the clamped position k of engaging part 275 of engaging recessed part 276, expand shape in being formed as entering towards rotary actuation direction.By making engaging recessed part 276 and engaging part 275 nip and easily engage in this wise, and the thrust avoiding clutch components 274 and tween drive spindle 271 to occur due to large driving counter-force etc. in advance and together backboard change position and making situation about easily departing from the engaging of engaging part 275.

Claims (38)

1. a crawler belt stretch adjusting device for crawler travel device, comprising:

Ground connection runner (124,125,126), is rotatably arranged at a laterally side of track-frame (122);

Guide member (152), the laterally side that the above-mentioned ground connection runner being positioned at above-mentioned track-frame (122) is positioned at, is supported by above-mentioned track-frame (122);

Tensioning frame (151), the fore-and-aft direction along track-frame is bearing on guide sections part (152) sliding freely;

Tension wheel (127), the wheel body support (150) being rotatably supported in mentioned strain adjustment framework (151) above and to crawler belt (129) applies supporting role;

Crawler belt guiding element (143), applies anticreep effect to above-mentioned crawler belt (129);

It is characterized in that,

Above-mentioned track-frame (122) arranges the guiding element installation portion (144) supporting above-mentioned crawler belt guiding element (143),

Above-mentioned guiding element installation portion (144) adjusts framework (151) and continuously arranges and support mentioned strain and adjust framework (151) with mentioned strain via link (157),

Possess multiple above-mentioned ground connection runner (124,125,126),

Above-mentioned guiding element installation portion (144) be arranged on above-mentioned fore-and-aft direction the rearmost position of above-mentioned multiple ground connection runner last ground connection runner (126), and the rear ground connection runner (125) more forward than this last ground connection runner (126) between,

Above-mentioned crawler belt guiding element (143) has:

Bar-shaped guiding element body (143a), is positioned between the guide wheel body of the pair of right and left of above-mentioned rear ground connection runner (125) to the guide wheel body of the pair of right and left of above-mentioned last ground connection runner (126);

Pipe link (143b), links above-mentioned guiding element body (143a) and above-mentioned guiding element installation portion (144),

Above-mentioned crawler belt guiding element (143) applies locking effect by the axle raised (129a) of above-mentioned guiding element body (143a) to above-mentioned crawler belt (129) and carries out the anticreep of above-mentioned crawler belt (129).

2. crawler belt stretch adjusting device as claimed in claim 1, is characterized in that, look from the side, and a part for the last ground connection runner (126) of the rearmost position in a part for above-mentioned tension wheel (127) and multiple above-mentioned ground connection runner repeats.

3. crawler belt stretch adjusting device as claimed in claim 1, it is characterized in that, above-mentioned crawler belt guiding element (143) is made by integrally casting above-mentioned guiding element body (143a) and above-mentioned pipe link (143b).

4. a crawler belt stretch adjusting device for crawler travel device, comprising:

Ground connection runner (124,125,126), is rotatably arranged at a laterally side of track-frame (122);

Guide member (152), the laterally side that the above-mentioned ground connection runner being positioned at above-mentioned track-frame (122) is positioned at, is supported by above-mentioned track-frame (122);

Tensioning frame (151), the fore-and-aft direction along track-frame is bearing on guide sections part (152) sliding freely;

Tension wheel (127), the wheel body support (150) being rotatably supported in mentioned strain adjustment framework (151) above and to crawler belt (129) applies supporting role;

Crawler belt guiding element (143), applies anticreep effect to above-mentioned crawler belt (129);

It is characterized in that,

Above-mentioned track-frame (122) arranges the guiding element installation portion (144) supporting above-mentioned crawler belt guiding element (143),

Above-mentioned guiding element installation portion (144) adjusts framework (151) and continuously arranges and support mentioned strain and adjust framework (151) with mentioned strain via link (157),

The axle that above-mentioned wheel body support (150) possesses the form of bifurcation supporting above-mentioned tension wheel (127) on two horizontal sides props up wheel fork (156), be arranged on above-mentioned axle props up strengthening rib (158) on the periphery of wheel fork (156),

Above-mentioned strengthening rib (158) is arranged on above-mentioned axle abreast in the mode of upper and lower two-stage and props up on wheel fork (156),

Possess tension adjustment mechanism, described tension adjustment mechanism is arranged along guide sections part (152) and mentioned strain adjustment framework (151), relative to guide sections part (152) slide control mentioned strain adjustment framework (151),

The end being in mentioned strain adjustment framework (151) side of mentioned strain adjusting mechanism is arranged to be positioned between the above-mentioned strengthening rib (158) of higher level side and the above-mentioned strengthening rib (158) of subordinate side,

Possess the fastener (153a) arranged along the above-mentioned strengthening rib (158) of higher level side and the above-mentioned strengthening rib (158) of subordinate side, above-mentioned end is locked to above-mentioned fastener (153a).

5. crawler belt stretch adjusting device as claimed in claim 4, is characterized in that, the leading section of mentioned strain adjustment framework (151) is fixed on the above-mentioned strengthening rib (158) of higher level side with the state of the lower surface of the above-mentioned strengthening rib (158) along higher level side.

6. crawler belt stretch adjusting device as claimed in claim 4, is characterized in that,

Possess the support (154) mentioned strain adjusting mechanism being supported on guide sections part (152),

Above-mentioned support (154) is arranged on the position of repeating with above-mentioned link (157) on above-mentioned fore-and-aft direction.

7. crawler belt stretch adjusting device as claimed in claim 5, is characterized in that,

Possess the support (154) mentioned strain adjusting mechanism being supported on guide sections part (152),

Above-mentioned support (154) is arranged on the position of repeating with above-mentioned link (157) on above-mentioned fore-and-aft direction.

8. crawler belt stretch adjusting device as claimed in claim 4, is characterized in that,

Possess the support (154) mentioned strain adjusting mechanism being supported on guide sections part (152),

Above-mentioned support (154) is with on the upper surface being fixed on guide sections part (152) along the upper surface of guide sections part (152) and the mode of side surface and side surface.

9. crawler belt stretch adjusting device as claimed in claim 5, is characterized in that,

Possess the support (154) mentioned strain adjusting mechanism being supported on guide sections part (152),

Above-mentioned support (154) is with on the upper surface being fixed on guide sections part (152) along the upper surface of guide sections part (152) and the mode of side surface and side surface.

10. a crawler belt stretch adjusting device for crawler travel device, comprising:

Ground connection runner (124,125,126), is rotatably arranged at a laterally side of track-frame (122);

Guide member (152), the laterally side that the above-mentioned ground connection runner being positioned at above-mentioned track-frame (122) is positioned at, is supported by above-mentioned track-frame (122);

Tensioning frame (151), the fore-and-aft direction along track-frame is bearing on guide sections part (152) sliding freely;

Tension wheel (127), the wheel body support (150) being rotatably supported in mentioned strain adjustment framework (151) above and to crawler belt (129) applies supporting role;

Crawler belt guiding element (143), applies anticreep effect to above-mentioned crawler belt (129);

It is characterized in that,

Above-mentioned track-frame (122) arranges the guiding element installation portion (144) supporting above-mentioned crawler belt guiding element (143),

Above-mentioned guiding element installation portion (144) adjusts framework (151) and continuously arranges and support mentioned strain and adjust framework (151) with mentioned strain via link (157),

Mode sliding guidance mentioned strain adjustment framework (151) that guide sections part (152) more leaves from guide sections part (152) with above-mentioned tension wheel (127) and more rises for above-mentioned track-frame (122).

The crawler belt stretch adjusting device of 11. 1 kinds of crawler travel devices, comprising:

Ground connection runner (124,125,126), is rotatably arranged at a laterally side of track-frame (122);

Guide member (152), the laterally side that the above-mentioned ground connection runner being positioned at above-mentioned track-frame (122) is positioned at, is supported by above-mentioned track-frame (122);

Tensioning frame (151), the fore-and-aft direction along track-frame is bearing on guide sections part (152) sliding freely;

Tension wheel (127), the wheel body support (150) being rotatably supported in mentioned strain adjustment framework (151) above and to crawler belt (129) applies supporting role;

Crawler belt guiding element (143), applies anticreep effect to above-mentioned crawler belt (129);

It is characterized in that,

Above-mentioned track-frame (122) arranges the guiding element installation portion (144) supporting above-mentioned crawler belt guiding element (143),

Above-mentioned guiding element installation portion (144) adjusts framework (151) and continuously arranges and support mentioned strain and adjust framework (151) with mentioned strain via link (157),

Above-mentioned guiding element installation portion (144) passing through is set up derby and forms on the transverse side of above-mentioned track-frame (122),

Above-mentioned guiding element installation portion (144), the end of this guiding element installation portion (144) is provided with three binder bolts (145) side by side along the above-below direction of above-mentioned track-frame (122) and fore-and-aft direction triangle configuration ground, thus supports the union lever (143b) of above-mentioned crawler belt guiding element (143).

12. as claim 1-3,10, crawler belt stretch adjusting device as described in 11 any one, it is characterized in that, possess tension adjustment mechanism and support (154), described tension adjustment mechanism is arranged along guide sections part (152) and mentioned strain adjustment framework (151), relative to guide sections part (152) slide control mentioned strain adjustment framework (151), mentioned strain adjusting mechanism is supported on guide sections part (152) by described support (154)

Above-mentioned support (154) is arranged on the position of repeating with above-mentioned link (157) on above-mentioned fore-and-aft direction.

13. crawler belt stretch adjusting devices as described in any one of claim 1-11, it is characterized in that, above-mentioned link (157) is made up of the parts of tabular.

14. crawler belt stretch adjusting devices as claimed in claim 13, it is characterized in that, above-mentioned link (157) is made up of upside sheet metal member (157a) and downside sheet metal member (157b), the side of described upside sheet metal member (157a) applies stopping function towards the lower surface of guide sections part (152) and mentioned strain adjustment framework (151), and described downside sheet metal member (157b) is clipped in above-mentioned upside sheet metal member (157a) and between the support (144a) be made up of the upper surface of above-mentioned guiding element installation portion (144).

15. crawler belt stretch adjusting devices as described in any one of claim 1-11, is characterized in that, above-mentioned guiding element installation portion (144) is arranged on the below of mentioned strain adjustment framework (151), support mentioned strain adjustment framework (151) from below.

16. as claim 1-3,10, crawler belt stretch adjusting device as described in 11 any one, it is characterized in that, possess tension adjustment mechanism and support (154), described tension adjustment mechanism is arranged along guide sections part (152) and mentioned strain adjustment framework (151), relative to guide sections part (152) slide control mentioned strain adjustment framework (151), mentioned strain adjusting mechanism is supported on guide sections part (152) by described support (154)

Above-mentioned support (154) is with on the upper surface being fixed on guide sections part (152) along the upper surface of guide sections part (152) and the mode of side surface and side surface.

17. crawler belt stretch adjusting devices as described in any one of claim 3-11, is characterized in that possessing multiple above-mentioned ground connection runner (124,125,126),

Look from the side, a part for the last ground connection runner (126) of the rearmost position in a part for above-mentioned tension wheel (127) and multiple above-mentioned ground connection runner repeats.

18. crawler belt stretch adjusting devices as claimed in claim 17, is characterized in that,

When mentioned strain adjustment framework (151) slides relative to guide sections part (152), above-mentioned tension wheel (127) and above-mentioned last ground connection runner (126) are deenergized enough repetitions from the side.

19. as claim 1-3,10, crawler belt stretch adjusting device as described in 11 any one, it is characterized in that possessing tension adjustment mechanism, described tension adjustment mechanism relative to guide sections part (152) slide control mentioned strain adjustment framework (151),

Mentioned strain adjusting mechanism is configured in the opposition side of above-mentioned track-frame (122) relative to the residing side of mentioned strain adjustment framework (151), arranges along guide sections part (152) and mentioned strain adjustment framework (151).

20. crawler belt stretch adjusting devices as described in claim 4 or 5, is characterized in that,

Mentioned strain adjusting mechanism is configured in the opposition side of above-mentioned track-frame (122) relative to the residing side of mentioned strain adjustment framework (151), arranges along guide sections part (152) and mentioned strain adjustment framework (151).

21. as claim 1-3,10, crawler belt stretch adjusting device as described in 11 any one, it is characterized in that possessing tension adjustment mechanism, described tension adjustment mechanism relative to guide sections part (152) slide control mentioned strain adjustment framework (151),

Mentioned strain adjusting mechanism is made up of tension adjustment axle (155), and the fastener (153a) of mentioned strain adjusting shaft (155) from the horizontal sidepiece being darted at above-mentioned wheel body support (150) is until the support (154) that is arranged on guide sections part (152) and installing.

22. crawler belt stretch adjusting devices as described in claim 4 or 5, it is characterized in that, mentioned strain adjusting mechanism is made up of tension adjustment axle (155), and the fastener (153a) of mentioned strain adjusting shaft (155) from the horizontal sidepiece being darted at above-mentioned wheel body support (150) is until the support (154) that is arranged on guide sections part (152) and installing.

The crawler belt stretch adjusting device of 23. 1 kinds of crawler travel devices, comprising:

Ground connection runner (124,125,126), is rotatably arranged at a laterally side of track-frame (122);

Guide member (152), the laterally side that the above-mentioned ground connection runner being positioned at above-mentioned track-frame (122) is positioned at, is supported by above-mentioned track-frame (122);

Tensioning frame (151), the fore-and-aft direction along track-frame is bearing on guide sections part (152) sliding freely;

Tension wheel (127), the wheel body support (150) being rotatably supported in mentioned strain adjustment framework (151) above and to crawler belt (129) applies supporting role;

Crawler belt guiding element (143), applies anticreep effect to above-mentioned crawler belt (129);

It is characterized in that,

The guiding element installation portion (144) supporting above-mentioned crawler belt guiding element (143) is supported on above-mentioned transverse direction one side of above-mentioned track-frame (122),

Above-mentioned guiding element installation portion (144) adjusts framework (151) and arranges and support mentioned strain continuously and adjust framework (151) with mentioned strain via the link (157) linked with above-mentioned guiding element installation portion (144),

When mentioned strain adjustment framework (151) slides relative to guide sections part (152), above-mentioned tension wheel (127), to deenergize from the side enough repetitions with the last ground connection runner (126) being positioned at the last side of above-mentioned fore-and-aft direction in above-mentioned multiple ground connection runner

The end of above-mentioned tension wheel (127) side in guide sections part (152) is supported on above-mentioned track-frame (122) from the position that above-mentioned tension wheel (127) is farther by above-mentioned link (157) on above-mentioned fore-and-aft direction compared with above-mentioned last ground connection runner (126)

The end of the side contrary with above-mentioned tension wheel (127) in guide sections part (152), is supported on above-mentioned track-frame (122) independently with the end of above-mentioned tension wheel (127) side in guide sections part (152),

Above-mentioned link (157) supports mentioned strain adjustment framework (151) sliding freely.

24. crawler belt stretch adjusting devices as claimed in claim 23, is characterized in that, above-mentioned guiding element installation portion (144) is supported on above-mentioned transverse direction one side of above-mentioned track-frame,

The end of above-mentioned tension wheel (127) side in guide sections part (152) is supported by the link (157) being linked to above-mentioned guiding element installation portion (144).

25. crawler belt stretch adjusting devices as claimed in claim 24, is characterized in that, above-mentioned link (157) supports the end of above-mentioned tension wheel (127) side in guide sections part (152) from below.

26. crawler belt stretch adjusting devices as claimed in claim 23, it is characterized in that, the position of overhang bracket between above-mentioned last ground connection runner (126) and the rear ground connection runner (125) adjacent with above-mentioned last ground connection runner (126) of above-mentioned tension wheel (127) side in guide sections part (152).

27. crawler belt stretch adjusting devices as claimed in claim 23, it is characterized in that, the end of the side contrary with above-mentioned tension wheel (127) in guide sections part (152) and the rear ground connection runner (125) adjacent with above-mentioned last ground connection runner (126) compared be supported on above-mentioned track-frame from the position that above-mentioned tension wheel (127) is farther.

28. crawler belt stretch adjusting devices as claimed in claim 23, is characterized in that, above-mentioned track-frame (122) has supporting arm (122a), (122a) of the front and back a pair of supporting guide sections part (152) in described transverse direction one side,

The end of the side contrary with above-mentioned tension wheel (127) in guide sections part (152) is supported by the above-mentioned supporting arm (122a) of front side.

29. crawler belt stretch adjusting devices as claimed in claim 28, is characterized in that, the supporting arm (122a) of above-mentioned front side supports the end of the side contrary with above-mentioned tension wheel (127) in guide sections part (152) from below.

30. crawler belt stretch adjusting devices as claimed in claim 28, is characterized in that, the supporting arm (122a) of above-mentioned front side is linked to described transverse direction one side of above-mentioned track-frame (122).

31. crawler belt stretch adjusting devices as claimed in claim 28, it is characterized in that, on the above-below direction of above-mentioned track-frame (122), the end of with above-mentioned tension wheel (127) the contrary side of above-mentioned supporting arm (122a) in the position lower than the end of above-mentioned tension wheel (127) side in guide sections part (152), supporting guide sections part (152) of front side.

32. crawler belt stretch adjusting devices as claimed in claim 23, is characterized in that, above-mentioned track-frame (122) has supporting arm (122a), (122a) of the front and back a pair of supporting guide sections part (152) in described transverse direction one side,

Above-mentioned guiding element installation portion (144) is supported on above-mentioned transverse direction one side of above-mentioned track-frame (122),

Guide sections part (152) utilize be linked to the link (157) of above-mentioned guiding element installation portion (144) and front and back a pair supporting arm (122a), (122a) and be supported on above-mentioned track-frame (122).

33. crawler belt stretch adjusting devices as claimed in claim 32, is characterized in that, the above-mentioned supporting arm (122a) of rear side is from side supporting guide sections part (152).

34. crawler belt stretch adjusting devices as claimed in claim 32, is characterized in that, guide sections part (152) is supported in the position of above-mentioned supporting arm (122a) between above-mentioned link (157) and the above-mentioned supporting arm (122a) of front side of rear side.

35. crawler belt stretch adjusting devices as claimed in claim 32, is characterized in that, the above-mentioned supporting arm (122a) of rear side is linked to the upper surface of above-mentioned track-frame (122).

36. crawler belt stretch adjusting devices as claimed in claim 23, is characterized in that, above-mentioned link (157) more extends to above-mentioned tension wheel (127) side than the end of above-mentioned tension wheel (127) side in guide sections part (152).

37. crawler belt stretch adjusting devices as claimed in claim 23, is characterized in that, above-mentioned guiding element installation portion (144) is supported on above-mentioned transverse direction one side of above-mentioned track-frame,

Possess crawler belt guiding element (143), described crawler belt guiding element (143) is supported on above-mentioned guiding element installation portion (144) and applies anticreep effect to above-mentioned crawler belt,

Possess the link (157) that one end is linked to above-mentioned guiding element installation portion (144),

Guide sections part (152) is at least formed as the open cross sectional shape in below in the end of above-mentioned tension wheel (127) side,

The other end of above-mentioned link (157) links the end of above-mentioned tension wheel (127) side in guide sections part (152) from below, form the bottom of the end of above-mentioned tension wheel (127) side in guide sections part (152), and support the end of above-mentioned tension wheel (127) side in guide sections part (152).

38. crawler belt stretch adjusting devices as claimed in claim 37, is characterized in that, above-mentioned link (157) more extends to above-mentioned tension wheel (127) side than the end of above-mentioned tension wheel (127) side in guide sections part (152).