CN102845179A - Grain recovery part work car of combine-harvester - Google Patents

Abstract

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

Description

The grain recoverer of combine drives structure

The application is to be dividing an application of September 25, application number in 2008 are 200810149742.5, denomination of invention is Operation Van patent application the applying date

Technical field

The present invention relates to a kind of Operation Van with the right side and left lateral motion device, more specifically, relate to a kind of steering operation structure of Operation Van, to the right and the left lateral motion device apply speed difference and carry out the steering operation of body.

Background technology

In the combine as an example of Operation Van, as JP2000-335268A is disclosed, have: the right side and left lateral motion device (Fig. 1 and Fig. 2 1); The 1st turning mechanism (Fig. 2 45), to the right and the left lateral motion device applies speed difference and body is turned; The 2nd turning mechanism (Fig. 2 49,50), to the right and the left lateral motion device apply than the large speed difference of the 1st turning mechanism body turned.

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

Thus, when steering operation spare is operated into straight carry and puts, to the right and the left lateral motion device transmit the power of identical speed and equidirectional, thereby body directly advances.

In the 1st state, if steering operation spare is for example operated to the right, then the 1st turning mechanism becomes duty, utilize the speed difference of the right side and left lateral motion device, make body change direction to the right, steering operation spare is operated larger to the right, and the speed difference of the right side and left lateral motion device is larger, and body changes direction to the right with less radius of turn.In the 2nd state, if steering operation spare is for example operated to the right, then the 2nd turning mechanism becomes duty, and is same as described above, and body also changes direction to the right.

As JP2000-335268A, have to the right and the left lateral motion device applies in the situation of the 1st and the 2nd turning mechanism of speed difference, there is room for improvement aspect the raising of the operability of turn performance and the operation of turning.

Summary of the invention

The object of the invention is to, in the steering operation structure of Operation Van, have to the right and the left lateral motion device apply the 1st and the 2nd turning mechanism of speed difference and have the 1st state that can set the 1st turning mechanism work or the situation of the turning set mechanism of the 2nd state of the 2nd turning mechanism work under, realize the raising of the operability of the turn performance of Operation Van and the operation of turning.

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

Have: the right side and left lateral motion device; The 1st turning mechanism, to the right and the left lateral motion device applies speed difference and body is turned; The 2nd turning mechanism, to the right and the left lateral motion device apply body turned.

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

Has controlling organization, in the 1st state, with steering operation spare from straight carry put more by to the right or the larger mode of speed difference of left operation, the right side and left lateral motion device operate the 1st turning mechanism, in the 2nd state, with steering operation spare from straight carry put more by to the right or the larger mode of speed difference of left operation, the right side and left lateral motion device operate the 2nd turning mechanism.

In the 1st state, corresponding with the unit operation amount of steering operation spare, poor based on the unit speed of the 1st turning mechanism, constitute in regional medium and small, the zone in the steering lock side of steering operation spare of directly advancing position side of steering operation spare large.

In the 2nd state, corresponding with the unit operation amount of steering operation spare, poor based on the unit speed of the 2nd turning mechanism, constitute in regional medium and small, the zone in the steering lock side of steering operation spare of directly advancing position side of steering operation spare large.

The variation characteristic that the unit speed of the 1st state is poor is set as different variation characteristics with the poor variation characteristic of the unit speed of the 2nd state.

According to above-mentioned the 1st feature structure, in the 1st state (the 2nd state), if steering operation spare is (left side) operation by to the right, then the 1st turning mechanism (the 2nd turning mechanism) becomes duty, by the speed difference of the right side and left lateral motion device, make body (left side) change direction to the right, (left side) operation is larger by to the right for steering operation spare, the speed difference of the right side and left lateral motion device is larger, make body with little radius of turn to the right (left side) change direction.

At this moment, in the zone of directly advancing position side the state of operation steering operation spare (only putting a little to the right or the state of left operation steering operation spare from straight carry), the speed difference of the right side and left lateral motion device is smaller, become in the ratio body of the operation of steering operation spare more to the right (left side) change nyctitropic state, so the such state of the inching of the direction of the body when being applicable to directly advance.This is specially adapted to the 1st state.

In addition, the state of operation steering operation spare in the zone of steering lock side (putting to the right or the left state that significantly operates steering operation spare from straight carry), the speed difference of the right side and left lateral motion device is larger, become in the ratio body of the operation of steering operation spare with little radius of turn to the right (left side) change nyctitropic state, so be applicable to change hastily the state of the direction of body.This is specially adapted to the 2nd state.

And then according to above-mentioned the 1st feature structure, the variation characteristic that the unit speed of the 1st state is poor is set as different variation characteristics with the poor variation characteristic of the unit speed of the 2nd state.

Thus, a situation arises (occurrence features) for the right side when putting to steering lock operation steering operation spare from straight carry and the speed difference of left lateral motion device, in the 1st and the 2nd state, be different, so, a situation arises (occurrence features) that identical formation is compared with speed difference above-mentioned in the 1st and the 2nd state, 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 speed based on 1st and 2nd turning mechanism corresponding with the unit operation amount of steering operation spare is poor, less in the zone of directly advancing position side of steering operation spare, larger in the zone of the steering lock side of steering operation spare, 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 operating type and set the 1st and the 2nd suitable state, can realize the turn performance of Operation Van and the lifting of the operability that operates of turning.

In the 2nd feature structure of the present invention, in the zone of directly advancing position side of steering operation spare, the poor variation characteristic of unit speed of setting the 1st and the 2nd state in the poor little mode of unit speed of poor ratio the 2nd state of the unit speed of the 1st state.This is more favourable aspect following.

In the 1st state, in the zone of directly advancing position side the state of operation steering operation spare (only putting a little to the right or the state of left operation steering operation spare from straight carry), the speed difference of the right side and left lateral motion device is smaller, become the ratio in the operation of steering operation spare, body more to the right (left side) changes nyctitropic state, so the state of the inching of the direction of the body when being applicable to directly advance.

At this moment, according to above-mentioned the 2nd feature structure, to the right and the left lateral motion device apply smaller speed difference and make in the 1st state that body turns, can obtain state as described above, so, the inching of the direction of the body of the 1st state when directly advancing is being consistent aspect the characteristic (characteristic that the direction of body changes not too largely), the inching of the direction of the body in the time of can having not harmony sense ground directly not advance for the driver.

Therefore, the operability of the turn performance of Operation Van and the operation of turning is improved more.

In the 3rd feature structure of the present invention, the 1st turning mechanism is to shallow turn mechanism (grand turn mechanism), this shallows turn mechanism to the right or side's direction of the opposing party's transmission of left lateral motion device and the right side or left lateral motion device is identical and the power of low speed, and the 2nd turning mechanism is to the right or the arrestment mechanism braked of left lateral motion device.

In the 4th feature structure of the present invention, the 1st turning mechanism is to shallow turn mechanism, this shallows turn mechanism to the right or side's direction of the opposing party's transmission of left lateral motion device and the right side or left lateral motion device is identical and the power of low speed, the 2nd turning mechanism is reversing device, and this reversing device to the right or the power of side's opposite direction of the opposing party's transmission of left lateral motion device and the right side or left lateral motion device.

If also have above-mentioned the 3rd feature structure or the 4th feature structure except having the 2nd feature structure, then by shallowing turn mechanism and arrestment mechanism or reversing device, the turning performance that can make the 1st and the 2nd state is fully different, sets the 1st and the 2nd suitable state so be easy to corresponding with the state on operation ground or operating type.

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 operating type and set the 1st and the 2nd suitable state, can realize the turn performance of Operation Van and the raising of the operability that operates of turning.

In the 5th feature structure of the present invention, except above-mentioned the 2nd feature structure, also has following such formation.

The 1st turning mechanism is to shallow turn mechanism, this shallows turn mechanism to the right or side's direction of the opposing party's transmission of left lateral motion device and the right side or left lateral motion device is identical and the power of low speed, and the 2nd turning mechanism is to the right or the arrestment mechanism braked of left lateral motion device.Have reversing device, this reversing device to the right or the power of side's opposite direction of the opposing party's transmission of left lateral motion device and the right side or left lateral motion device.

Constitute and to utilize the turning set mechanism to set the 3rd state that use is shallowed turn the 2nd state of the 1st state of mechanism, use arrestment mechanism, used reversing device.In the zone of directly advancing position side of steering operation spare, the poor variation characteristic of unit speed of setting the 2nd and the 3rd state in the poor little mode of unit speed of poor ratio the 3rd state of the unit speed of the 2nd state.

If based on above-mentioned the 5th feature structure, then by having the mechanism of shallowing turn, arrestment mechanism and reversing device, the turning performance that can make the 1st, 2,3 states is fully different, so with the state on operation ground or operating type is corresponding and options enlarges, be easy to set the 1st, 2,3 suitable states.

In addition, in the zone of directly advancing position side of steering operation spare, the unit speed of the 1st state is poor be set to poor less than the unit speed of the 2nd state, the unit speed of the 2nd state is poor to be set to poor littlely than the unit speed of the 3rd state, and the poor variation characteristic of the unit speed of the 1st, 2,3 states is set to different.Thus, make the differing greatly of turning performance of the 1st, 2,3 states, with the state on operation ground or operating type is corresponding and options enlarges, be easy to set the 1st, 2,3 suitable states.

Therefore, by making options enlarge this point by the 1st, 2,3 states and making the difference of the turning performance of the 1st, 2,3 states increase this point, be easy to corresponding with the state on operation ground or operating type and set the 1st, 2,3 suitable states, can realize the turn performance of Operation Van and the raising of the operability that operates of turning.

In the 6th feature structure of the present invention, except above-mentioned the 2nd feature structure, also has following such formation.

The 1st turning mechanism is to shallow turn mechanism, this shallows turn mechanism to the right or side's direction of the opposing party's transmission of left lateral motion device and the right side or left lateral motion device is identical and the power of low speed, and the 2nd turning mechanism is to the right or the arrestment mechanism braked of left lateral motion device.Have reversing device, this reversing device to the right or the power of side's opposite direction of the opposing party's transmission of left lateral motion device and the right side or left lateral motion device.

Constitute and to utilize the turning set mechanism to set the 3rd state that use is shallowed turn the 2nd state of the 1st state of mechanism, use arrestment mechanism, used reversing device.In the zone of directly advancing position side of steering operation spare, the identical mode of unit speed poor with the unit speed of the 2nd state and the 3rd state is set the poor variation characteristic of unit speed of the 2nd and the 3rd state.

If based on above-mentioned the 6th feature structure, then by having the mechanism of shallowing turn, arrestment mechanism and reversing device, the turning performance that can make the 1st, 2,3 states is fully different, so with the state on operation ground or operating type is corresponding and options enlarges, be easy to set the 1st, 2,3 suitable states.

In addition, in the zone of directly advancing position side of steering operation spare, the unit speed of the 1st state is poor to be set to poor littlely than the unit speed of the 2nd state, and the poor unit speed with the 3rd state of the unit speed of the 2nd state is poor to be set to identical speed difference.Thus, it is unnecessary large that the difference of the turning performance of the 1st, 2,3 states is become, and is easy to corresponding with the state on operation ground or operating type and sets the 1st, 2,3 suitable states.

Therefore, by make options enlarge this point by the 1st, 2,3 states, and the difference that does not make the turning performance of the 1st, 2,3 states becomes unnecessary large this point, be easy to corresponding with the state on operation ground and operating type and set the 1st, 2,3 suitable states, can realize the turn performance of Operation Van and the raising of the operability that operates of turning.

Thereby on one side read clear and definite other feature structure and the advantage of following explanation on one side with reference to accompanying drawing.

In the following description, as long as no different expressing, the direction of then forwards directly advancing (advancing) with the combine as an example of Operation Van is called fore-and-aft direction as benchmark, to be called with the horizontal direction of this fore-and-aft direction orthogonal left and right directions (perhaps transverse direction), the direction vertical with fore-and-aft direction and left and right directions will be called above-below direction.

Description of drawings

Fig. 1～Fig. 6 is the figure of expression the 1st embodiment.

Fig. 1 is the unitary side view of combine.

Fig. 2 is the vertical profile front view of gearbox, the right side and Left Drive case.

Fig. 3 is near the vertical profile front view of shallowing turn clutch (grand turn clutch), brake, reversing clutch, the right side and left side clutch of gearbox.

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

Fig. 5 is the figure of the relation of expression gear lever, turning-bar, turning mode switch, hydrostatic stepless speed change device and hydraulic pressure unit.

Fig. 6 is the figure of the following solid line of expression, namely represents the solid line (shallowing turn (grand turn)) of the relation of the operating position of turning-bar and the operating current of proportional control valve (shallowing turn the operating pressure of clutch), the solid line (wheel one stops one and turns pivot turn (pivot turn)) of the relation of the operating position of expression turning-bar and the operating current (operating pressure of brake) of proportional control valve, the solid line (pivot turn of wheel a positive and a negative (spin turn)) of the relation of the operating position of expression turning-bar and the operating current (operating pressure of reversing clutch) of proportional control valve.

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

Fig. 7 is the end view of workover rig.

Fig. 8 is the end view of crawler travel device.

Fig. 9 is the vertical view of crawler travel device.

Figure 10 is the end view at crawler travel device rear portion.

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

Figure 12 is the vertical profile end view of crawler belt stretch adjusting device.

Figure 13 is the vertical view of protruding guiding element installation constitution.

Figure 14 is the stereogram of protruding guiding element installation portion and attaching parts.

Figure 15 is the vertical view of wheel body support.

Figure 16 is the end view of wheel body support.

Figure 17～35th, the figure of expression the 3rd embodiment.

Figure 17 is the unitary side view of combine.

Figure 18 is the end view of cereal box.

Figure 19 is the vertical view of cereal box.

Figure 20 is the stereogram of seeing cereal box from the inboard the place ahead of body.

Figure 21 is the skeleton diagram of transmission system.

Figure 22 is the vertical profile end view of expression end screw rod and the connection structure of being connected conveyer.

Figure 23 is the expansion profile of the bindiny mechanism of the vertical conveyer of expression and horizontal conveyer.

Figure 24 is the rearview of cereal box.

Figure 25 is the vertical view that the expression threshing transports the turning driving structure of device.

Figure 26 is the rearview of the section that transports of expression cereal box.

Figure 27 is the stereogram at the rear portion of expression cereal box.

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

Figure 29 is the cross-sectional vertical view of the clutch on-state of the transmission system of expression from engine to end screw rod.

Figure 30 is the cross-sectional vertical view of the clutch dissengaged positions of the transmission system of expression from engine to end screw rod.

Figure 31 is the vertical profile end view of the drive structure of expression end screw front end section.

Figure 32 is the front view that expression flows down the driving structure of guided plate.

Figure 33 is the front view of seeing from axis direction of clutch components.

Figure 34 is the profile of clutch components.

Figure 35 is the expanded view of the engaging recessed part in the expression clutch components.

Embodiment

Below, with reference to the description of drawings embodiments of the present invention.A plurality of embodiments below have been described, but have thought that the combination of feature of the feature of one of them embodiment and other embodiments is also contained within the scope of the present invention.

[the 1st embodiment]

[1]

As shown in Figure 1, be equivalent to moving device by right and left crawler travel device 1() front portion of the body of supporting, support freely around transverse axis core P1 lifting and to extract framework 2, have lifting and drive the lifting pressure cylinder 3 that extracts framework 2, extract section 4 extracting framework 2 upper supports.Right side in the front portion of body has Drive Section 5, has sheller unit 8 in the left side at the rear portion of body, has cereal box 9 on the right side at the rear portion of body, consists of the combine from off-type as an example of Operation Van.

Then, gearbox 10 is described.

As shown in Figures 1 and 2, has gearbox 10 near the central authorities about the front portion of body, be formed with the recess 10a of the poor shape of ladder on the top of the right side of gearbox 10, linking in the mode of the recess 10a that enters into gearbox 10 has hydrostatic stepless speed change device 11.Have right and left support 10b in the outside of the bottom of gearbox 10, the right and left support 10b of the right side and Left Drive case 14 and gearbox 10 links and stretches out to the front side.

Such as Fig. 1 and shown in Figure 2, right and left axle box 15 link with the right side and Left Drive case 14 and to the right and the left side stretch out, on the end in the right side of right and left axle box 15 and left side, have the sprocket wheel 1a that drives right and left crawler travel device 1.Outside in the bottom of gearbox 10 has linking part 10c, and from the linking part 10c of gearbox 10 until the right side and Left Drive case 14, linking has attaching parts 13.

[2]

The structure of the transmission system (directly entering system) in the gearbox 10 then, is described.

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

As shown in Figure 2, on the power transmission shaft 27 on the top that is bearing in gearbox 10, relatively be embedded with high gear 25 and low-speed gear 26 outside the rotation freely, 25 engagements of travelling gear 23 and high gear, travelling gear 24 and low-speed gear 26 engagements, gearshift parts 28 are by spline structure and one rotation and outer being embedded on the power transmission shaft 27 sliding freely.Consist of secondary speed-changing device by travelling gear 23 and high gear 25, travelling gear 24 and low-speed gear 26, gearshift parts 28, by gearshift parts 28 and high speed and low- speed gear 25,26 are meshed, the power of power shaft 27 can speed change be passed to power transmission shaft 27 for height two-stage (high speed position and low-speed position).Usually, to the position slide gearshift parts 28 of high gear 25 engagement, thereby the setting high-speed position.

Such as Fig. 2 and shown in Figure 3, the lower support power transmission shaft 29 along gearbox 10 is fixed with travelling gear 31 in the left side of power transmission shaft 29, is fixed with travelling gear 30 in the left side of power transmission shaft 27, travelling gear 30,31 engagements.On power transmission shaft 29, relatively be embedded with right and left output gear 32R, 32L outside the rotation freely, on the right side and left side of right and left output gear 32R, 32L, right and left engaging piece 33R, 33L are by spline structure and one rotation and outer being embedded on the power transmission shaft 29 sliding freely.Between right output gear 32R and right engaging piece 33R, consist of right side clutch 34, between left output gear 32L and left engaging piece 33L, consist of left side clutch 34.

As shown in Figure 2, from the right and left support 10b of gearbox 10 until the right side and Left Drive case 14 are supported with power transmission shaft 35, inside at gearbox 10, be fixed on travelling gear 36 and right and left output gear 32R, 32L engagement on the power transmission shaft 35, on the right side and the inside of Left Drive case 14, travelling gear 37 is fixed on the power transmission shaft 35.From the right side and Left Drive case 14 until right and left axle box 15 is supported with right and left axletree 38, on the right side and the inside of Left Drive case 14, be fixed on travelling gear 39 and travelling gear 37 engagements on right and the left axletree 38.In the inside of right and left axle box 15, right and left axletree 38 to the right and the 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 side of right and left axletree 38 and the end in left side.

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

[3]

Then, the right side and left side clutch 34 are described.

As shown in Figure 3, be formed with spline part 29a on the right side of power transmission shaft 29 and the outer surface of left side, right and left engaging piece 33R, 33L can the one rotation reach freely slidably outer being embedded on the spline part 29a of power transmission shaft 29, and accepting parts 40 can one be embedded on the spline part 29a of power transmission shaft 29 outward rotatably.

As shown in Figure 3, on the position of accepting parts 40 sides of right and left engaging piece 33R, 33L, dispose a plurality of recesses along circumferencial direction, going up separately of the recess of right and left engaging piece 33R, 33L, dispose doubly spring 41 in inboard and the outside, by accepting 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 be subject to the application of force.By right and left engaging piece 33R, 33L and right and left output gear 32R, 32L engagement, become the drive state of the right side and left side clutch 34, the power of power transmission shaft 29 is passed to the right side and left crawler travel device 1 via the right side and left side clutch 34.

As shown in Figure 3, piston 42 can be configured between right and left output gear 32R, 32L and the power transmission shaft 29 freely slidably, piston 42 and right and left engaging piece 33R, 33L butt, stride across right and left engaging piece 33R, 33L until piston 42 and be inserted with spring catch 43, so that piston 42 rotates integratedly with right and left engaging piece 33R, 33L.

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

[4]

The structure of the transmission system (turning system) in the gearbox 10 then, is described.

As shown in Figures 2 and 3, be supported with power transmission shaft 44 across gearbox 10, the relatively freely gear part engagement of travelling gear 45 and the peripheral part of right engaging piece 33R of the outer right side that is embedded in power transmission shaft 44 of rotation, between power transmission shaft 44 and travelling gear 45, have the clutch of shallowing turn 46(and be equivalent to the 1st turning mechanism, and be equivalent to shallow turn mechanism (grand turn mechanism)).Shallowing turn clutch 46, to be constituted as friction multi-plate, is operating as drive state by supplying with working oil, is operating as dissengaged positions by discharging working oil.

As shown in Figures 2 and 3, turning clutch box 47 is rotation outer being embedded on the power transmission shaft 29 freely relatively, is fixed on the travelling gear 47a engagement of travelling gear 48 and the peripheral part of turning clutch box 47 on the power transmission shaft 44.Turning clutch box 47 is constituted as left-right symmetry, has the right side and left-hand bend clutch 49 between turning clutch box 47 and right and left output gear 32R, 32L.It is multi-plate that the right side and left-hand bend clutch 49 are constituted as friction, is operating as drive state by supplying with working oil.In this case, in the right side and left-hand bend clutch 49, friction plate is closely configuration mutually, even working oil is discharged from, the right side and left-hand bend clutch 49 also become half drive state.

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

As shown in Figures 2 and 3, have brake 50(in the left side of power transmission shaft 44 and be equivalent to the 2nd turning mechanism) (being equivalent to arrestment mechanism).It is multi-plate that brake 50 is constituted as friction, is operating as on-position by supplying with working oil, is operating as disarm state by discharging working oil.

Thus, as shown in Figures 2 and 3, when brake 50 was operating as on-position, via power transmission shaft 44 and travelling gear 48, turning clutch box 47 became on-position.On the right side or left side clutch 34 when being operating as dissengaged positions, the right side or left-hand bend clutch 49 and being operating as drive state, right or left output gear 32R, 32L become on-position.

As shown in Figures 2 and 3, be fixed with travelling gear 51 in the left side of power transmission shaft 27, on the left side of power transmission shaft 44, relatively be embedded with travelling gear 52 outside the rotation freely, travelling gear 51,52 engagements have reversing clutch 53(and are equivalent to the 2nd turning mechanism between power transmission shaft 44 and travelling gear 52) (being equivalent to reversing device).It is multi-plate that reversing clutch 53 is constituted as friction, is operating as drive state by supplying with working oil, is operating as dissengaged positions by discharging working oil.

Thus, as shown in Figures 2 and 3, when reversing clutch 53 is operating as drive state, the power of power transmission shaft 27 is passed to turning clutch box 47 via travelling gear 51,52, reversing clutch 53, power transmission shaft 44 and travelling gear 48 as the power opposite with power transmission shaft 29 direction of rotation.On the right side or left side clutch 34 when being operating as dissengaged positions, the right side or left-hand bend clutch 49 and being operating as drive state, be passed to right or left output gear 32R, 32L with the power of power transmission shaft 29 rightabout rotations.

[5]

The operation of hydrostatic stepless speed change device 11 then, is described.

As shown in Figure 5, the pump 11P of hydrostatic stepless speed change device 11 constitute to neutral position N, from neutral position N march forward F high-speed side and retreat the freely infinitely variable speeds of high-speed side of R, the motor 11M of hydrostatic stepless speed change device 11 constitutes freely speed change of height two-stage ground.Have operation hydrostatic stepless speed change device 11 pump 11P swash plate hydraulic cylinder 59, to the control valve 60 of hydraulic cylinder 59 to row's operation element oil, the gear lever 61 that is provided in Drive Section 5 is connected with control valve and is mechanically connected.Thus, by operation gear lever 61, control valve 60 is operated, hydraulic cylinder 59 actions, and the swash plate of the pump 11P of hydrostatic stepless speed change device 11 is operated to the position corresponding with the operating position of gear lever 61.

As shown in Figure 5, possess operation hydrostatic stepless speed change device 11 motor 11M swash plate hydraulic cylinder 62, to the control valves 63 of hydraulic cylinder 62 to the solenoid operated of row's operation element oil, possess varying speed switch 61a in the holding part of gear lever 61, the operation signal of the varying speed switch 61a of gear lever 61 is input to control device 64(and is equivalent to controlling organization) in.Thus, by the varying speed switch 61a of operation gear lever 61,64 operations of control valve 63 controlled devices, hydraulic cylinder 62 actions, the swash plate of the motor 11M of hydrostatic stepless speed change device 11 is operated at a high speed and low-speed position.

Turning mode switch 78 of record in [7] described later [8] [9] [10], shallow turn (grand turn), wheel one stops one and turns in each state of pivot turn (pivot turn) and wheel a positive and a negative pivot turn (spin turn), can select to shallow turn state by turning mode switch 78, wheel one stops one and turns pivot turn state and wheel a positive and a negative pivot turn state, be to utilize the varying speed switch 61a of gear lever 61 swash plate of the motor 11M of hydrostatic stepless speed change device 11 to be operated the state of low-speed position.If utilize the varying speed switch 61a of gear lever 61 swash plate of the motor 11M of hydrostatic stepless speed change device 11 is operated the state of high speed position, then irrelevant with the operating position of turning mode switch 78, select the state of shallowing turn.

[6]

Then, illustrate to the right and left side clutch 34(is right and left engaging piece 33R, 33L), the right side and left-hand bend clutch 49, shallow turn clutch 46, brake 50, reversing clutch 53 to the hydraulic pressure unit 57 of row's operation element oil.

As shown in Figure 4, on the power shaft (not shown) of hydrostatic stepless speed change device 11, linking has supply pump (not shown) and hydraulic pump 56, constitute the power shaft by hydrostatic stepless speed change device 11, drive supply pump and hydraulic pump 56, the working oil of supply pump is supplied to hydrostatic stepless speed change device 11.Such as Fig. 2 and shown in Figure 3, hydraulic pressure unit 57 links with the outer surface of the left horizontal sidepiece of gearbox 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.

Such as Fig. 2 and shown in Figure 3, power transmission shaft 29,44 left part connect the left cross side of gearbox 10, and be inserted into the inside of hydraulic pressure unit 57, from the left part of power transmission shaft 29 until the right side and left side clutch 34(are right and left engaging piece 33R, 33L), the right side and left-hand bend clutch 49, possess oil circuit 29b in the inside of power transmission shaft 29.From the left part of power transmission shaft 44 until shallow turn clutch 46 and reversing clutch 53, possesses oil circuit 44a in the inside of power transmission shaft 44.In the inside of hydraulic pressure unit 57, possesses brake 50 in the end of power transmission shaft 44.

As shown in Figure 4, in the inside of hydraulic pressure unit 57, possess right-hand bend control valve 67, left-hand bend control valve 68, safety valve 69, feather 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, link surface (faying face) at the left horizontal sidepiece of hydraulic pressure unit 57 and gearbox 10 is formed with a plurality of oil circuits (not shown), and the right side and left-hand bend control valve 67,68, safety valve 69, feather valve 70 are connected on the oil circuit 66 that is connected with outside pipe arrangement 58 side by side via the oil circuit of link surface (faying face).Link surface (faying face) at the left horizontal sidepiece of hydraulic pressure unit 57 and gearbox 10 is formed with the discharge oil circuit, and the working oil of safety valve 69 and feather valve 70 is back to gearbox 10 via above-mentioned discharge oil circuit.

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

As shown in Figure 4, the right side and left-hand bend control valve 67,68 constitute and can freely operate the solenoid operated of supplying with position 67a, 68a and drain position 67b, 68b, to drain position 67b, the 68b application of force.Feather valve 70 constitutes the solenoid operated that can freely operate off-position 70a and drain position 70b, to the off-position 70a application of force.From the right side and left-hand bend control valve 67,68 and the oil circuit 29b of power transmission shaft 29 between on the oil circuit 75 of branch, be connected in series proportional control valve 71 and turning switching control valve 72, turning switching control valve 72 is via the oil circuit of link surface (faying face) and the oil circuit 44a of power transmission shaft 44, with shallow turn clutch 46 and be connected with reversing clutch and be connected, turning switching control valve 72 is connected with brake 50 via the oil circuit 76 of hydraulic pressure unit 57.

As shown in Figure 4, proportional control valve 71 constitutes solenoid operated, can carry out the flow-control (pressure control) of working oil.Turning switching control valve 72 constitutes freely to operate and shallows turn position 72a, wheel one and stop a pilot operated that turns pivot turn position 72b and wheel a positive and a negative pivot turn position 72c, to shallowing turn the position 72a application of force.Operation will consist of guide operating valve 73 to wheel one mode that turns pivot turn position 72b of stopping being supplied to turning switching control valve 72 from guide's working oil of oil circuit 75 branches, and operation will consist of guide operating valve 74 to the mode of wheel a positive and a negative pivot turn position 72c being supplied to turning switching control valve 72 from guide's working oil of oil circuit 75 branches.

The right side and left-hand bend control valve 67,68, feather valve 70, proportional control valve 71, guide operating valve 73,74, [7] [8] [9] [10] are described by control device 64 operations as described later.

[7]

Then, straight moving condition based on turning-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 left artificially operation turning-bar 77(freely is equivalent to steering operation spare), the operating position of turning-bar 77 is input in the control device 64, and turning-bar 77 constitutes and can operate freely straight carry and put N, the right side and left the 1st turning position R1, L1, right side and a left side the 2nd turning position R2, L2.In Drive Section 5, be equipped with turning mode switch 78(and be equivalent to the set mechanism of turning), the operating position of turning mode switch 78 is input in the control device 64, and turning mode switch 78 possesses the position of shallowing turn (being equivalent to the 1st state), wheel one stops one and turns 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).

Such as Fig. 4 and shown in Figure 5, irrelevant with the operating position of turning mode switch 78, if turning-bar 77 is operated into straight carry and puts N, then the right side and left-hand bend control valve 67,68 are operated into drain position 67b, 68b, feather valve 70 is operated into drain position 70b, working oil is from the right side and left side clutch 34(is right and left engaging piece 33R, 33L), the right side and left-hand bend clutch 49 discharge, the right side and left side clutch 34(right and left engaging piece 33R, 33L) be operating as drive state, the right side and left-hand bend clutch 49 are operating as half drive state.Shallow turn and reversing clutch 46,53 is operating as dissengaged positions by proportional control valve 71, brake 50 is operating as disarm state.

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

[8]

Then, the state of shallowing turn based on turning-bar 77 is described.

Such as Fig. 4 and shown in Figure 5, if with turning mode switch 78 operation to shallowing turn the position, the switching control valve of then turning 72 is by guide operating valve 73,74 and be operated into and shallow turn position 72a.Thus, if turning-bar 77 is operated into right the 1st turning position R1, the control valve 67 of then turning right is operated into supplies with position 67a, feather valve 70 is operated into off-position 70a, working oil is supplied to the right engaging piece 33R of right side clutch 34() and right-hand bend clutch 49, the right engaging piece 33R of right side clutch 34() be operating as dissengaged positions, right-hand bend clutch 49 is operating as drive state.

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

Such as Fig. 4 and shown in Figure 5, if right the 1st turning position R1 is arrived in turning-bar 77 operations, the control valve 67 of then turning right as mentioned above is operated into supplies with position 67a, feather valve 70 is operated into off-position 70a, simultaneously, working oil begins to shallow turn position 72a via proportional control valve 71 and turning switching control valve 72() and be supplied to and shallow turn clutch 46, turning-bar 77 is more from right the 1st turning position R1 the 2nd turning position R2 operation to the right, shallow turn the operating pressure of clutch 46 more by proportional control valve 71 boost operations (as shown in Figure 6, the solid line A1(of the relation of the operating current (shallowing turn the operating pressure of clutch 46) of the operating position of reference expression turning-bar 77 and proportional control valve 71 is shallowed turn state)).

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

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

Then, if turning-bar 77 is operated right the 2nd turning position R2 side from right the 1st turning position R1, the operating pressure of shallowing turn 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 clutch 46) power, right output gear 32R is by from the power drive of shallowing turn clutch 46.Under this state, compared with right output gear 32R by from the left engaging piece 33L of left side clutch 34() power drive, at right output gear 32R by in from the power-actuated situation of shallowing turn clutch 46, right output gear 32R is driven with low speed, body is shallowed turn to the right, more by the 2nd turning position R2 side operation to the right, the radius of turn of body becomes less to turning-bar 77.

Such as Fig. 4 and shown in Figure 5, if left the 1st turning position L1 is arrived in turning-bar 77 operations, the control valve 68 that then turns left is operated into supplies with position 68a, feather valve 70 is operated into off-position 70a, working oil is supplied to the left engaging piece 33L of left side clutch 34() and left-hand bend clutch 49, the left engaging piece 33L of left side clutch 34() be operating as dissengaged positions, left-hand bend clutch 49 is operating as drive state.Meanwhile, carry out operation same as described above, body changes direction at leisure left.If turning-bar 77 is operated left the 2nd turning position L2 side from left the 1st turning position L1, then carry out operation same as described above, body is shallowed turn left.

[9]

Then explanation stops one based on the wheel one of turning-bar 77 and turns the pivot turn state.

Such as Fig. 4 and shown in Figure 5, if being stopped one to wheel one, turning mode switch 78 operation turns the pivot turn position, the switching control valve of then turning 72 is by guide operating valve 73,74 and be operated into wheel one and stop and turn pivot turn position 72b.Thus, if right the 1st turning position R1 is arrived in turning-bar 77 operations, the control valve 67 of then turning right is operated into supplies with position 67a, feather valve 70 is operated into off-position 70a, working oil is supplied to the right engaging piece 33R of right side clutch 34() and right-hand bend clutch 49, the right engaging piece 33R of right side clutch 34() be operating as dissengaged positions, right-hand bend clutch 49 is operating as drive state.In this case, left-hand bend clutch 49 is half drive states, so body and above-mentioned [8] similarly change direction at leisure to the right.

Such as Fig. 4 and shown in Figure 5, if right the 1st turning position R1 is arrived in turning-bar 77 operations, then as mentioned above, right-hand bend control valve 67 is operated into supplies with position 67a, and feather valve 70 is operated into off-position 70a, simultaneously, working oil stops one via proportional control valve 71 and turning switching control valve 72(wheel one and turns pivot turn position 72b) begin to be supplied to brake 50, turning-bar 77 is more from right the 1st turning position R1 the 2nd turning position R2 side operation to the right, the operating pressure of brake 50 is more by proportional control valve 71 boost operations (as shown in Figure 6, the solid line A2(wheel one of the relation of the operating current (operating pressure of brake 50) of the operating position of reference expression turning-bar 77 and proportional control valve 71 stops one and turns the pivot turn state)).

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

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

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

Such as Fig. 4 and shown in Figure 5, if left the 1st turning position L1 is arrived in turning-bar 77 operations, the control valve 68 that then turns left is operated into supplies with position 68a, feather valve 70 is operated into off-position 70a, working oil is supplied to the left engaging piece 33L of left side clutch 34() and left-hand bend clutch 49, the left engaging piece 33L of left side clutch 34() be operating as dissengaged positions, left-hand bend clutch 49 is operating as drive state.Meanwhile, carry out operation same as described above, body changes direction at leisure left.If turning-bar 77 is operated left the 2nd turning position L2 side from left the 1st turning position L1, then carry out operation same as described above, body stops one to left wheel one and turns pivot turn.

Such as Fig. 4 and shown in Figure 5, has pole changer 77a in the holding part of turning-bar 77.As described in above-mentioned [8], be operated at turning mode switch 78 and shallow turn the position, from right (left side) the 1st turning position R1(L1) (left side) the 2nd turning position R2(L2 to the right) right side or the left side of operation turning-bar 77 shallow turn the state, produces the needs with less semidiameter turn.

In this case, such as Fig. 4 and shown in Figure 5, with turning-bar 77 from right (left side) the 1st turning position R1(L1) (left side) the 2nd turning position R2(L2 to the right) under the state of operation, if the pole changer 77a of pressing operation turning-bar 77, the switching control valve of then turning 72 is operated into wheel one and stops one and turn pivot turn position 72b from shallowing turn position 72a, and body to the right (left side) wheel one stops one and turns pivot turn.This wheel one stops one and turns the pivot turn state only during the pole changer 77a of pressing operation turning-bar 77, if hand is taken away operation from the pole changer 77a of turning-bar 77, the switching control valve of then turning 72 is stopped one from wheel one and is turned pivot turn position 72b and be operated to and shallow turn position 72a, and body returns the state of shallowing turn.

[10]

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

Such as Fig. 4 and shown in Figure 5, if wheel a positive and a negative pivot turn position is arrived in 78 operations of turning mode switch, the switching control valve of then turning 72 is arrived wheel a positive and a negative pivot turn position 72c by guide operating valve 73,74 operations.Thus, if right the 1st turning position R1 is arrived in turning-bar 77 operations, the control valve 67 of then turning right is operated into supplies with position 67a, feather valve 70 is operated into off-position 70a, working oil is supplied to the right engaging piece 33R of right side clutch 34() and right-hand bend clutch 49, the right engaging piece 33R of right side clutch 34() be operating as dissengaged positions, right-hand bend clutch 49 is operating as drive state.In this case, left-hand bend clutch 49 is half drive states, so body and above-mentioned [8] similarly change direction at leisure to the right.

Such as Fig. 4 and shown in Figure 5, if right the 1st turning position R1 is arrived in turning-bar 77 operations, then as mentioned above, right-hand bend control valve 67 is operated into supplies with position 67a, and feather 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) begin to be supplied to reversing clutch 53, turning-bar 77 is more from right the 1st turning position R1 the 2nd turning position R2 operation to the right, the operating pressure of reversing clutch 53 is more by proportional control valve 71 boost operations (as shown in Figure 6, solid line A3(wheel a positive and a negative pivot turn of the relation of the operating current (operating pressure of reversing clutch 53) of the operating position of reference expression turning-bar 77 and proportional control valve 71)).

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

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

Then, at turning-bar 77 by from right the 1st turning position R1 the 2nd turning position R2 side operation to the right, when the operating pressure of reversing clutch 53 is boosted a little, as shown in Figures 2 and 3, surpass from the left engaging piece 33L of left side clutch 34(from the power of reversing clutch 53) power, right output gear 32R is by the power drive from reversing clutch 53.Under this state, to driven in the other direction, body is the pivot turn of wheel a positive and a negative to the right with respect to left output gear 32L for right output gear 32R, turning-bar 77 the 2nd turning position R2 side operation more to the right, and the radius of turn of body becomes less.

Such as Fig. 4 and shown in Figure 5, if left the 1st turning position L1 is arrived in turning-bar 77 operations, the control valve 68 that then turns left is operated into supplies with position 68a, feather valve 70 is operated into off-position 70a, working oil is supplied to the left engaging piece 33L of left side clutch 34() and left-hand bend clutch 49, the left engaging piece 33L of left side clutch 34() be operating as dissengaged positions, left-hand bend clutch 49 is operating as drive state.Meanwhile, carry out operation same as described above, body changes direction at leisure left.If turning-bar 77 is operated left the 2nd turning position L2 side from left the 1st turning position L1, then carry out operation same as described above, body turns pivot turn to left wheel one positive.

[11]

In above-mentioned [8], [9], [10] state of shallowing turn of putting down in writing, wheel one stops one and turns in pivot turn state and the wheel a positive and a negative pivot turn state, the relation of the operating current of the operating position of turning-bar 77 and proportional control valve 71 (shallowing turn the operating pressure of clutch 46) is that the solid line A1(of Fig. 6 is shallowed turn state) represented relation, the relation of the operating current of the operating position of turning-bar 77 and proportional control valve 71 (operating pressure of brake 50) is that the solid line A2(wheel one of Fig. 6 stops one and turns the pivot turn state) represented relation, the relation of the operating current of the operating position of turning-bar 77 and proportional control valve 71 (operating pressure of reversing clutch 53) is solid line A3(wheel a positive and a negative pivot turn state of Fig. 6) represented relation.

Solid line A1(is shallowed turn state), A2(wheel one stops one and turns the pivot turn state), A3(wheel a positive and a negative pivot turn state), become formula B1 shown below, B2,2 times such curves of B3.

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

B2(A2(wheel one stops one and turns the 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 turning-bar 77

Y1: the operating current of proportional control valve 71 (shallowing turn the operating pressure of clutch 46)

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

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

A11～a33: positive constant

Thus, at the state of shallowing turn, wheel one stops one and turns in pivot turn state and the 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 turning-bar 77 is (by shallowing turn clutch 46, brake 50 and reversing clutch 53 and unit speed right and that left crawler travel device 1 occurs is poor) (unit speed of the 1st and the 2nd state is poor), right and left the 1st turning position R1 at turning-bar 77, L1 side (straight carry put the N side) regional medium and small is at the right of turning-bar 77 and a left side the 1st turning position R2, large in the zone of L2 side (steering lock side).

In this case, in positive constant a11～a33, what is called

a11>a12>a13

a21>a22>a23

a31>a32>a33

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

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

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

Stopping one at the state of shallowing turn, the wheel one of above-mentioned [the 1st embodiment] turns in pivot turn state and the wheel a positive and a negative pivot turn state, if any one that also can constitute state shown below (1) (2) (3) set up, then do not carry out the operation to high speed position (with reference to above-mentioned [5]) based on the motor 11M of the hydrostatic stepless speed change device 11 of the varying speed switch 61a of gear lever 61.

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

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

(3) turning-bar 77 is operated to the state of right the 2nd turning position R2 side (left side the 2nd turning position L2 side) from the centre position between the right side the 1st and right the 2nd turning position R1, the R2 (centre position between a left side the 1st and left the 2nd turning position L1, the L2).

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

Stopping one at the state of shallowing turn, the wheel one of above-mentioned [the 1st embodiment] turns in pivot turn state and the wheel a positive and a negative pivot turn state, if any one that also can constitute state shown below (1) (2) (3) set up, then do not carry out the operation to high speed position (with reference to above-mentioned [5]) based on the motor 11M of the hydrostatic stepless speed change device 11 of the varying speed switch 61a of gear lever 61.

(1) by the action of shallowing turn clutch 46, brake 50 and reversing clutch 53, produces the state of speed difference at right and left crawler travel device 1.

(2) by the action of shallowing turn clutch 46, brake 50 and reversing clutch 53, the gait of march that produces speed difference and body at right and left crawler travel device 1 is the state of the high speed more than the setting speed.

(3) by the action of shallowing turn clutch 46, brake 50 and reversing clutch 53, producing speed difference and this speed difference at right and left crawler travel device 1 is the state of setting speed more than poor.

[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 constitute and have the clutch of shallowing turn 46 and brake 50 without reversing clutch 53.If consist of in this wise, then shallowing turn clutch 46 is the 1st turning mechanism, and brake 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 constitute and have the clutch of shallowing turn 46 and reversing clutch 53 without brake 50.If consist of in this wise, then shallowing turn 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 constitute wheel one and stop a characteristic (formula B2(A2(wheel one stops and turns the pivot turn state) that turns the 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 constitute formula B1(A1(and shallow turn state)), formula B2(A2(wheel one stops one and turns the pivot turn state)), formula B3(A3(wheel a positive and a negative pivot turn state)) do not constitute curve 2 times, obtain characteristic as shown in Figure 6 by the different a plurality of straight lines (1 function) of combination slope.

[the 2nd embodiment]

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

In the 2nd embodiment, the crawler belt stretch adjusting device having rotation and be arranged in freely the ground connection runner 124,125 of a horizontal side of track-frame 122,126 crawler travel device is characterized by,

Have: guide member 152 is positioned at the horizontal side that the above-mentioned ground connection runner 124,125,126 of above-mentioned track-frame 122 is positioned at, by above-mentioned track-frame 122 supportings; Tension adjustment framework 151 is bearing on the guide sections part 152 sliding freely along the track-frame fore-and-aft direction; Regulating wheel 127, rotation are supported in freely mentioned strain and adjust on the wheel body support 150 of framework 151 and apply supporting role to crawler belt 129; Tension adjustment mechanism is adjusted framework 151 with respect to guide sections part 152 slidable adjustment mentioned strains,

For above-mentioned wheel body support 150, has the form of bifurcation at the above-mentioned regulating wheel 127 of two horizontal side upper supports.

As above-mentioned track takeup, for example, the device (with reference to paragraph [0019], Fig. 3) that has JP2005-335614A to put down in writing.

In the crawler belt stretch adjusting device that the document is put down in writing, have: carriage can be inserted into the rear end of track-frame slidingly back and forth; Straining pulley, pine turn freely the earth's axis and prop up on this carriage.

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

In this crawler belt stretch adjusting device, have the fulcrum that stretches out to a horizontal side from carriage, it is distolateral to make straining pulley be bearing in stretching out of this fulcrum, thereby, the horizontal side that the earthy runner that makes straining pulley be positioned at track bracket is positioned at is so that crawler belt suitably is wound on the straining pulley.

In this crawler belt stretch adjusting device, if when turning etc. when high tension occurs crawler belt, at the support unit of the fulcrum of regulating wheel etc. larger distortion occurs, it is mobile and crawler belt comes off easily that departing from of regulating wheel then occurs.For this reason, regulating wheel is supported securely, even in order at crawler belt the movement that departs from that regulating wheel can not occur high tension yet occurs.In above-mentioned track tension adjusting device in the past, the fulcrum of regulating wheel only is supported at the one-sided of regulating wheel, if will make the supporting of regulating wheel firm, then makes fulcrum chap etc. and weight is increased.

Corresponding therewith, formation according to present embodiment, employing is positioned at the guide member 152 of the horizontal side that the ground connection runner 124,125,126 of track-frame 122 is positioned at, thereby the wheel body support 150 that can make tension adjustment framework 151 has the form of bifurcation at two horizontal side upper support regulating wheels 127, and the horizontal side that the ground connection runner 124,125,126 that makes straining pulley 127 be positioned at track bracket 122 is positioned at is so that crawler belt 129 can suitably be wound on the straining pulley 127.Thus, the fulcrum of regulating wheel 127 is supported in two horizontal sides of regulating wheel 127, even if adopt fulcrum than small-sized regulating wheel 127 in the past, tension adjustment framework 151 etc., even and if at crawler belt 129 high tension occurs, regulating wheel 127 is supported securely and do not depart from movement.

Therefore, make the supporting of regulating wheel 127 firmly be difficult for occuring the come off situation that waits and can obtain light-weighted crawler belt stretch adjusting device from the consideration of regulating wheel supporting construction aspect of crawler belt 129.

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

Observe the load based on crawler belt 129 of regulating wheel 127, be making a concerted effort of the tension force that occurs of the position along the direction of track-frame 122 and the tension force that occurs for the position of the direction that tilts with respect to track-frame 122 being positioned at than regulating wheel 127 more close downsides than regulating wheel 127 more close upsides being positioned at of crawler belt 129, apply to regulating wheel as the tension force of crawler belt 129.

If based on this formation, then because the tension force of the crawler belt 129 and direction of the load that applies to regulating wheel 127 is the direction along the mobile direction of tension adjustment framework 151 guided members 152 guiding, or with its direction that approaches, be difficult between guide member 152 and tension adjustment framework 151, twisting, and can slidable adjustment tension adjustment framework 151.

Therefore, can obtain a kind of track tension adjusting device, this track tension adjusting device can make and be difficult for twisting between guide member 152 and the tension adjustment framework 151 and smooth and easy and carry out easily tension adjustment.

And then, the mentioned strain guiding mechanism to be adjusted framework 151 with respect to mentioned strain be configured on the opposite side of the side that is positioned at above-mentioned track-frame 122, and adjust framework 151 along guide sections part 152 and mentioned strain and install, this is favourable in the following areas.

According to this formation, can be not be subject to obstruction ground operation tension adjustment mechanism based on track-frame 122 from the opposite side of a side that is positioned at respect to tension adjustment framework 151 and with track-frame 122.

Therefore, the operation of governing mechanism of tension 155 is carried out in the operation that can not be subject to track-frame 122 with hindering, thereby obtains and can smooth and easyly carry out tension adjustment and the crawler belt stretch adjusting device of operability excellence efficiently.

In addition, be provided with guiding element installation portion 144 at above-mentioned track-frame 122,144 of this guiding element installation portions are honoured the crawler belt guiding element 143 that crawler belt 129 applies the anticreep effect, on above-mentioned guiding element installation portion 144, possess the support 144a that applies supporting role to above-mentioned tension adjustment framework 151, this is favourable in the following areas.

Guiding element installation portion 144 supporting crawler belt guiding elements 143 are so have excellent intensity.Thus, according to the present invention, can as supporting device tension adjustment framework 151 be supported securely guiding element installation portion 144.

Therefore, can be by with the guiding element installation portion 144 simple structure as supporting device, obtain that tension adjustment framework 151 can be supported securely and the track tension adjusting device of carrying out swimmingly the tension adjustment of crawler belt 129.

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

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

This workover rig results rice or wheat etc.

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

When making the section of extracting 110 become the decline state body of advancing being advanced, extract section 110, by careless part 113 of each minute, import the upright paddy bar that extracts object and it is carried out pull-up process to the heaving mechanism 114 corresponding with minute careless part 113 in body transverse direction a plurality of heaving mechanisms 114 arranged side by side, to the upright paddy bar after being processed by each heaving mechanism 114 pull-up, extract processing by one the extracting device 115 of hairclipper shape, supply with from what extract device 115 to the top section of the threshing carrier chain 104a of threshing grain device 104 by feedway 116 and extract the paddy bar.

Sheller unit 104 transports the strain root side that extracts the paddy bar by threshing carrier chain 104a and to the body rear to clamping, supply with this fringe point side that extracts the paddy bar and carry out the threshing processing to threshing chamber (not shown).Cereal box 105 reclaims and stores the threshing grain that transports from sheller unit 104.

Fig. 8 is the end view of the crawler travel device 101 in left side.Fig. 9 is the vertical 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 the left side, has omitted the diagram of right side crawler travel device 101.As shown in these figures, crawler travel device 101 constitutes, and has: track-frame 122, via above-mentioned a pair of supporting arm 120,121 and link with above-mentioned organism frame 103; Drive rotation crawler driving whell 123 freely, above the place ahead of this track-frame 122, be bearing on the above-mentioned organism frame 103 via gearbox (not shown); 8 pines turn ground connection runner 124,125,126 freely, are bearing on the track-frame 122 side by side along the track-frame fore-and-aft direction on being positioned at of above-mentioned track-frame 122 advanced body lateral outer side one side's horizontal side; Regulating wheel 127, be arranged in above-mentioned 8 ground connection runners 124,125,126 the most close track-frame rear end side ground connection runner 126 the top, rear and be arranged on the rearward end of track-frame 122; The a pair of pine in front and back turns carrying roller 128,128 freely, be bearing in above the above-mentioned track-frame 122 on the above-mentioned organism frame 103, and having along a pair of carrying roller 128 of above-mentioned crawler driving whell 123, above-mentioned 8 ground connection runners 124,125,126, above-mentioned regulating wheel 127, above-mentioned front and back, 128 and the crawler belt 129 of the rubber system of reeling.

The supporting arm 120 of above-mentioned front side, via the rotation fulcrum 120a that the base portion of this supporting arm 120 and organism frame 103 rotations are linked freely and on the end of the opposite side of the side that links with above-mentioned supporting arm 120 of this rotation fulcrum 120a the one rotation coupled arm 130 of setting freely, with the pressure cylinder bar 131a interlock of hydraulic cylinder 131.

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

The supporting arm 121 of above-mentioned rear side, via the rotation fulcrum 121a that the base portion of this supporting arm 121 and organism frame 103 rotations are linked freely and on the end of the opposite side of the side that links with above-mentioned supporting arm 121 of this rotation fulcrum 121a the one rotation coupled arm 132 of setting freely, with the pressure cylinder bar 133a interlock of hydraulic cylinder 133.The free end side of the supporting arm 121 of rear side, the rear end side via payment connecting rod 134 with track-frame 122 links.

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

That is, about a pair of supporting arm 120,121 in crawler travel device 101,101 front and back by swinging operation, thereby the body of advancing tilts to transverse direction or fore-and-aft direction with respect to ground.

Namely, carry out swinging operation, so that about a side a pair of supporting arm 120,121 in front and back of crawler travel device 101 rise together or descend swing, and a pair of supporting arm 120 in front and back, 121 rising or descending stroke are identical, thereby a side's of the crawler travel device about making 101 track-frame 122 rises abreast or descends with respect to organism frame 103, advance a distolateral earth point with another distolateral crawler travel device 101 in the transverse direction of body as swinging fulcrum, and with respect to ground rise or fall.

Carry out swinging operation, so that about the supporting arm 120 of front side of crawler travel device 101 and a side of the supporting arm 121 of rear side rise or descend and swing, and about the supporting arm 120 of crawler travel device 101,121 rising or descending stroke are identical, thereby about the track-frame 122 of crawler travel device 101 swing up and down with respect to organism frame 103 as swinging fulcrum with the earth point of front, perhaps swings up and down with respect to organism frame 103 as swinging fulcrum with the earth point of rear end side, a wherein end of the fore-and-aft direction of the body of advancing with the other end as the swing fulcrum and with respect to ground rise or fall.

Then, the ground connection runner 126 that will be arranged in above-mentioned 8 ground connection runner 124,125,126 the most close track-frame rear end side is called last ground connection runner 126, will be arranged in ground connection runner 125 than above-mentioned 8 ground connection runner 124,125,126 above-mentioned last ground connection runner 126 position forward, that close with last ground connection runner 126 neighbours and be called rear ground connection runner 125 and describe.

Above-mentioned rear ground connection runner 125 and above-mentioned last ground connection runner 126, only pine turns and is bearing in freely on the track-frame 122, makes it can not lifting with respect to track-frame 122.

The ground connection runner 124 of removing above-mentioned last ground connection runner 126 and above-mentioned rear ground connection runner 125 in above-mentioned 8 ground connection runners 124,125,126, two ground connection runners 124 that the neighbour is closed, 124 groupings and form a runner group, two ground connection runners 124 of each runner group, 124 concentrate and with the state lower support that links by a cantilever connecting member 140 and track-frame 122 on track-frame 122.

Such as Fig. 9, shown in Figure 10, each above-mentioned cantilever connecting member 140 rotates via the connecting axle 141 that is positioned at the intermediate portion and to be bearing in freely on the track-frame 122.Form two ground connection runners 124 of each runner group, a side of 124 ground connection runner 124, pine turns on the position of the above-mentioned connecting axle 141 more close front of the ratio that is bearing in freely above-mentioned cantilever connecting member 140, the opposing party's ground connection runner 124, pine turn on the position of the above-mentioned connecting axle 141 more close rear end side of the ratio that is bearing in freely above-mentioned cantilever connecting member 140.

Thus, the ground connection runner 124 of removing above-mentioned last ground connection runner 126 and above-mentioned rear ground connection runner 125 in 8 ground connection runners 124,125,126, form two ground connection runners 124,124 of above-mentioned each runner group, be installed on the track-frame 122 by cantilever connecting member 140, by the swing of cantilever connecting member 140, with the axle core of above-mentioned connecting axle 141 as swinging fulcrum with respect to reciprocally lifting of track-frame 122.

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

Such as Fig. 8, shown in Figure 10, constitute corresponding to the above-mentioned crawler belt guiding element 142 of above-mentioned each runner group and to have: bar-shaped guiding element body 142a, between the guide wheel body of the pair of right and left of a side's of runner group ground connection runner 124 to the guide wheel body of the pair of right and left of the opposing party's ground connection runner 124; Connecting rod 142b links this guiding element body 142a and above-mentioned cantilever connecting member 140, and by guiding element body 142a, axle projection 129a, the 129a to about the crawler belt 129 applies the locking effect and carry out the anticreep of crawler belt 129.Corresponding to the crawler belt guiding element 142 of each runner group, by above-mentioned guiding element body 142a and above-mentioned connecting rod 142b are made with above-mentioned cantilever connecting member 140 integrally castings.

As shown in figure 10, constitute corresponding to the above-mentioned crawler belt guiding element 143 of above-mentioned last ground connection runner 126 and above-mentioned rear ground connection runner 125 and to have: bar-shaped guiding element body 143a, between the guide wheel body of the pair of right and left of rear ground connection runner 125 to the guide wheel body of the pair of right and left of last ground connection runner 126; Connecting rod 143b, the guiding element installation portion 144 that this guiding element body 143a and track-frame 122 are possessed links, and by guiding element body 143a, the axle projection 129a to about the crawler belt 129 applies the locking effect and carries out the anticreep of crawler belt 129.This crawler belt guiding element 143 is by integrally casting above-mentioned guiding element body 143a and above-mentioned connecting rod 143b and be made.

The above-mentioned guiding element installation portion 144 of track-frame 122 is set up metal derby and is consisted of at the transverse side of track-frame 122.This guiding element installation portion 144, above-below direction and fore-and-aft direction triangle configuration ground along track-frame 122 on the end of guiding element installation portion 144 are equipped with three binder bolts 145 side by side, thereby support the connecting rod 143b of above-mentioned crawler belt guiding element 143.

Crawler travel device 101, the crawler belt stretch adjusting device A with the present embodiment on the rear portion that is arranged on track-frame 122.

Fig. 9 represents the structure of overlooking of the crawler belt stretch adjusting device A of present embodiment.Figure 10 represents the structure of side-looking of the crawler belt stretch adjusting device A of present embodiment.Figure 11 is the vertical profile vertical view of the crawler belt stretch adjusting device A of present embodiment.Figure 12 is the vertical profile end 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 constitutes and has: above-mentioned regulating wheel 127; Framework 151 is adjusted in tensioning, turns by wheel body support 150 pines and supports freely this regulating wheel 127; Guide member 152 supports this tension adjustment framework 151; Tension adjustment axle 155, the fastener 153a from the horizontal sidepiece that is darted at above-mentioned wheel body support 150 installs until be arranged on the support 154 on the guide sections part 152.

Mentioned strain is adjusted framework 151 and is constituted, and except possessing above-mentioned wheel body support 150, also possesses frame body 151a, and this frame body 151a is made of the angle-steel tubing that a base portion distolateral and this wheel body support 150 links.

Figure 15 is the vertical view of above-mentioned wheel body support 150.Figure 16 is the end view 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 to have a pair of axle with the configuration on the two horizontal sides that are positioned at discretely regulating wheel 127 and prop 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 regulating wheels 127 of regulating wheel 127.That is, at two horizontal side bearing regulating wheels 127.

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

Such as Figure 12～shown in Figure 14, end and the mentioned strain of the side that the mentioned strain adjustment framework 151 of guide sections part 152 is given prominence to are adjusted framework 151, carry the attaching parts 157 on the support 144a that consists of in the upper surface by the above-mentioned installation portion 144 of track-frame 122 via the bottom, supported from below stop by above-mentioned support 144a.Above-mentioned attaching parts 157 are made of upside sheet metal member 157a and downside sheet metal member 157b, the side of described upside sheet metal member 157a applies stopping function to the lower surface of guide member 152 and tension adjustment framework 151, and described downside sheet metal member 157b is clipped between this upside sheet metal member 157a and the above-mentioned support 144a.

Mentioned strain is adjusted framework 151, and its frame body 151a is embedded in guide sections part 152 sliding freely, thereby guided member 152 support sliding freely, the medial surface sliding guidance of guided member 152 and along the fore-and-aft direction slip of track-frame 122.Tension adjustment framework 151, glide direction arranges according to the installation direction of guide member 157, thus regulating wheel 127 slides more to leave the state that more rises with respect to track-frame 122 from guide member 152.Namely, tension adjustment framework 151, be along the tension force at the position of the direction of track-frame 122 than regulating wheel 127 more close upsides and be positioned at than regulating wheel 127 more close downsides and for the tension force of track-frame 122 for the position of the direction that tilts, slide along the direction close with the direction of the load that applies to regulating wheel 127 by being positioned at of crawler belt 129.

Mentioned strain is adjusted axle 155, consisted of by thread spindle, this thread spindle is combined with the internal thread screw thread of the adjustment axle inserting hole that above-mentioned support 154 at guide member 152 arranges, during rotary manipulation, move along the track-frame fore-and-aft direction with respect to guide member 152 and apply by or draw effect to the above-mentioned fastener 153a of wheel body support 150, thereby, with respect to guide member 152 slidable adjustment tension adjustment frameworks 151.This tension adjustment axle 155 is configured on the opposite side of the side that is positioned at track-frame 122 with respect to tension adjustment framework 151, can not be subjected to operate based on the operating barrier of track-frame 122 from the body horizontal stroke outside of advancing of crawler travel device 101.

Generally speaking, crawler belt stretch adjusting device A by rotary manipulation tension adjustment axle 155, makes tension adjustment framework 151 by guide member 152 and attaching parts 157 sliding guidances and mobile the adjusting by this tension adjustment axle 155.At this moment, tension adjustment framework 151 slides along the direction that the direction with the load that applies to regulating wheel 127 approaches by the tension force of crawler belt 129, and is moving to be difficult for producing sliding in state of reversing between tension adjustment framework 151 and guide member 152.So regulating wheel 127 is regulated to its rear side shifting with respect to track-frame 122 and is pressed crawler belt 129 to more close moving device rear side, thereby to the tensile force that increases side adjustment crawler belt 129.Perhaps, regulating wheel 127 with respect to track-frame 122 forwards side be moved and regulate and pressing of crawler belt 129 weakened, thereby, to the tensile force that reduces side and adjust crawler belt 129.

Such as Figure 15, shown in Figure 16, above-mentioned wheel body support 150 props up wheel fork 156 and above-mentioned fastener 153a except possessing above-mentioned axle, also possesses: a pair of ribs 158,158 up and down is arranged on the outer circumferential side that axle props up wheel fork 156; The 2nd fastener 153b props up wheel fork 156 with respect to above-mentioned axle and is arranged on the opposite side of the side that is positioned at above-mentioned fastener 153a.Above-mentioned axle props up wheel fork 156 and above-mentioned fastener 153a and above-mentioned ribs 158 and above-mentioned the 2nd fastener 153b, by the investment casting casting and by integrally casting.

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

[other embodiments of the 2nd embodiment]

Also can replace above-mentioned embodiment, adopt the formation by grease pressure cylinder slidable adjustment tension adjustment framework 151, also can realize purpose of the present invention.Therefore, tension adjustment axle 155, grease pressure cylinder etc. is 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; grain recoverer driving structure for a kind of combine; about side by side configuration sheller unit 207 and cereal box 208; and on the front side of cereal box 208, laterally dispose engine 204; leading section to the end screw rod 210 of above-mentioned cereal box 208 transmits engine power; it is characterized by

Project output shaft 263 to body to horizontal foreign side from above-mentioned engine 204, and laterally support has intermediate propeller shaft 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 intermediate propeller shaft 271, and interlock links the body outside left of above-mentioned intermediate propeller shaft 271 and the leading section of end screw rod 210.

Grain recoverer as sheller unit drives structure; known have a following formation (for example with reference to JP9-205867A); roll up square side in the body of the intermediate propeller shaft of hanging the output shaft that interlock projects in linking from the engine of laterally configuration to body and the front side that laterally is provided in cereal box via driving-belt; and the input magazine that interlock links square side in the body of intermediate propeller shaft and is equipped with in the front portion of cereal box is passed to engine power via intermediate propeller shaft and input magazine the leading section of end screw rod.

In above-mentioned in the past structure, compare the position that is positioned at away from body side from the output shaft that engine projects with the end screw rod of cereal box, so engine is arranged on side in the body for the left and right sides weight balancing of body, then bears about the intermediate propeller shaft of engine power longer.

Particularly, constitute cereal box is rotated to body foreign side around vertical fulcrum at rear portion, thereby open significantly the horizontal sidepiece of sheller unit, and, the input part that can connect the outer square end of the body that consists of discretely intermediate propeller shaft and cereal box, the input part of cereal box automatically separates from middle power transmission shaft with the open interlock of the rotation of cereal box, the input part of cereal box automatically is connected with intermediate propeller shaft with the recovery rotation interlock of cereal box, in such formation, must prop up by other axle the pars intermedia that parts support intermediate propeller shaft accurately, so that staying the intermediate transmission shaft position of the length of body side when the rotation of cereal box is open does not change, the number of components that consists of drive structure increases, and cost up.

Relative therewith, if the formation according to present embodiment, even if then engine 204 is configured in side in the body, output shaft 263 also from engine 204 to body horizontal foreign side outstanding, therefore, crossbearer is approached along the body transverse direction in the interlock position of the leading section of the body outside left of the body inside line of the intermediate propeller shaft 271 of the front side of cereal box 208 and intermediate propeller shaft 271 and end screw rod 210, and intermediate propeller shaft 271 shortens.Short intermediate propeller shaft 271, the demand that supports therebetween reduces.

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

Preferably above-mentioned cereal box 208 being constituted can be around vertical fulcrum P rotation at rear, and the front portion of input magazine 251 with above-mentioned cereal box 208 linked, power shaft 254 and above-mentioned intermediate propeller shaft 271 in the body with the core shape ground above-mentioned input magazine 251 of arranged opposite possesses possess the clutch 273 that takes off from the shaft core direction card at its opposed position.This formation is favourable in the following areas.

If according to above-mentioned formation, then pass through cereal box 208 sideway swivel outside body, can automatically disconnect the interlock of intermediate propeller shaft 271 and end screw rod 210 and leave from sheller unit 207 significantly, can easily carry out the maintenance of the sidepiece of sheller unit 207 from open space.Acceptance is side-prominent in from input magazine 251 to body from the power shaft 254 of the power of intermediate propeller shaft 271, so correspondingly can make intermediate propeller shaft 271 shorter.

Below, illustrate in greater detail the 3rd embodiment.

Figure 17, the end view of seeing from the body right side of expression head feeding type combined harvester (whole culm discharging type combine-harvester).This combine constitutes, the section that extracts 203 of a plurality of strip harvesting part specifications links freely with the anterior lifting of the organism frame 202 of the crawler travel device 201 that possesses pair of right and left, former moving section 205 and the Drive Section 206 of engine 204 in being equipped with, the front portion, right side of above-mentioned organism frame 202 are housed, and, be equipped with sheller unit 207 in the left side of organism frame 202, and be equipped with the cereal box 208 of sheet metal structure in the position of the rear side of former moving section 205 on the right side of sheller unit 207, to be supplied to sheller unit 207 and carry out threshing and process by extracting paddy bar that section 203 extracts, the device 209 of winnowing of screw be raised to send by sheller unit 207 and is sorted the grain of recovery and it is fed into cereal box 208.

Such as Figure 20 and shown in Figure 24, above-mentioned cereal box 208 is seen at fore-and-aft direction, forms narrow shape under its underpart, and, on the right lateral surface of side in body, be formed with the lengthwise recess 208a that enters the above-mentioned device 209 of winnowing of configuration.Front and back at above-mentioned lengthwise recess 208a are formed with recess 208b, 208c, and this recess 208b, 208c avoids and to the interference at the outstanding device position of the right flank of sheller unit 207, be formed with the bulge 208d that increment is used on the top, the place ahead of lengthwise recess 208a.Thus, the left-hand face of cereal box 208 and the right side shape of sheller unit 207 are approached as far as possible, thereby can guarantee large container capacity.

Lower end at lower narrow 208e of above-mentioned cereal box 208, via fulcrum 210a front and back flatly support the end screw rod 210 of rearward sending the grain that stores is arranged, and along the top of end screw rod 210, via rotating fulcrum 212 swingingly support have that cross sectional shape forms chevron flow down guided plate 211.

Lower narrow 208e of cereal box 208, what be applied in grain flows down the above angle of inclination of angle of repose, so that the grain that stores does not have residual and is directed into end screw rod 210, and, the bottom that disposes lower narrow 208e to horizontal foreign side significantly from the horizontal wide center of container is so that screw rod of the above-mentioned end 210 is positioned at than organism frame 202 more in the outer part.The lower end part that makes in this wise lower narrow the 208e that accommodates end screw rod 210 is in than organism frame 202 more laterals, compare in the situation of the top of organism frame 202 with the lower end part of lower narrow 208e of cereal box 208, more the lowland arranges the bottom of lower narrow 208e of cereal box 208, thus, the container upper end position is improved and increase container height (lower-upper length), thus can capacity increasing.

The threshing grain that is equipped with screw at the rear of cereal box 208 transports device 213, this threshing grain transport device 213 will by the grain that end screw rod 210 is sent raise send after, horizontal transporting and outside machine, transporting.This threshing transports device 213, have the vertical conveyer 213A of the screw that is connected with the lower end, back of cereal box 208 and the horizontal conveyer 213B of the screw that is connected with the upper end of this vertical conveyer 213A, grain transports the integral body of device 213, can by with the screw rod axle center of vertical conveyer 213A with vertical fulcrum P of core centered by and rotary moving.

As shown in figure 22, link in the rear end, bottom of above-mentioned cereal box 208 the fulcrum 210a that supporting end screw rod 210 is arranged rearward end transport case 214, and the above-mentioned lower end boss portion 214a that transports case 214 is chimeric being bearing on the support 202a outstanding from organism frame 202 to body foreign side rotationally, and cereal box 208 can be supported rotatably around above-mentioned vertical fulcrum P.As shown in figure 28, has the support plate 215 that is consisted of by heavy-gauge sheeting at the bottom of cereal box 208 front surface, the bottom mounting of this support plate 215 is bearing on the upper surface of organism frame 202, and the gross weight of cereal box 208 is supported by organism frame 202 and support 202a in former and later two positions.

On above-mentioned support plate 215, can slide up and down to possess lock pin 220.Lock pin 220 is by spring 221 and downwards by the slip application of force; by inserting the bottom of lock pin 220 in the locking hole 222 on being arranged on organism frame 202 sides; cereal box 208 can be fixed on set threshing and reclaim the position; extract lock pin 220 by overcoming spring 221 from locking hole 222, can make cereal box 208 around vertical fulcrum P rotary moving and the maintenance position of the right side of open sheller unit 207 significantly.In addition, above-mentioned lock pin 220, by on pull out and rotate and can lock and remain on the metal bracket 223 that possesses on the support plate 215.

Such as Figure 17～Figure 19, shown in Figure 27, be fixed with the side cover 225 of covering container side surface in the lateral outer side binding of cereal box 208.On the bottom of side cover 225, linking has the lower side cover 226 that covers lower narrow the outside 208e of cereal box 208 from horizontal foreign side.On the rearward end of side cover 225, linking has rear portion side cover 227, and this rear portion side cover 227 covers grain from horizontal side and transports the major part of the vertical conveyer 213A of device 213, and possesses working light 228 and overall width lamp 229 etc.On the rearward position of vertical conveyer 213A, from the organism frame 202 vertical vertical frameworks 231 of cornue system of establishing, cover the back cover 230 of vertical conveyer 213A from the rear and should link fixing by vertical framework 231.At cereal box 208 around vertical fulcrum P during to the rotation of horizontal foreign side, shown in the imaginary line among Figure 19, with cereal box 208 integratedly the rear portion side cover 227 of rotary moving do not produce with fixing back cover 230 and interfere and change the rear over to.As shown in figure 28, on the leading section of lower side cover 226, can swing around vertical fulcrum a movable hood 232 openedly and closedly is installed, by opening this movable hood 232, above-mentioned lock pin 220 exposes, and can carry out locking operation and the locking of cereal box 208 and remove operation.

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

Such as Figure 22 and shown in Figure 26, in the above-mentioned bottom that transports case 214, be formed with access R, this access R will be directed into by the grain that end screw rod 210 is sent the longitudinal feed of vertical conveyer 213A to the transport zone of screw rod 236, this access R, the shape that transports mouthful 208f that transports the lower shape of case 214 and cereal box 208 forms respectively the Long Circle of lengthwise, to become the elongate shape of expanding 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, to possess and be inserted in the infeed screw rod 239 than the fulcrum 239a in the large footpath of fulcrum 236a of above-mentioned vertical fortune screw rod 236 by in the tote box 238 that consists of with the circular pipes in footpath with the tote box 235 of vertical conveyer 213A and consist of, possess the outlet 240 of downward direction opening in the top ends of tote box 238.The base end part of the upper end of the tote box 235 of vertical conveyer 213A and the tote box 238 of horizontal transveyer 213B is by connecting box 241 connection that is connected.Connecting box 241 comprises the upper end 241a of connecting box section on the upper end of the tote box 235 that is packed in vertical conveyer 213A and is packed in the cardinal extremity connecting box 241b of section on the base end part of the tote box 238 among the horizontal conveyer 213B, the cardinal extremity connecting box 214b of section can be around rotationally chimeric binding of horizontal fulcrum Q with respect to the upper end connecting box 241a of section, and horizontal conveyer 213B can swing up and down around above-mentioned horizontal fulcrum Q.

On above-mentioned horizontal fulcrum Q, be equipped with two supports in above-mentioned upper end the relay axis 242 on the 241a of case section and the cardinal extremity connecting box 241b of section in succession.Be equipped with the feeding impeller 243 that tilts with respect to horizontal fulcrum Q at this relay axis 242, and the two ends of relay axis 242 respectively with longitudinal feed to the cardinal extremity of the fulcrum 239a of the upper end of the fulcrum 236a of screw rod 236 and infeed screw rod 239 with constant speed bevel gear interlock.Thus, with the rotation interlock of end screw rod 210 longitudinal feed to screw rod 236 and infeed screw rod 239 by driven in synchronism, the grain of sending from cereal box 208 indulged conveyer 213A raise send after, discharged from outlet 240 by horizontal horizontal the transporting of conveyer 213B.

The relay axis of above-mentioned in succession case 241 is inserted logical position, form the tote box 238 large footpaths than tote box 235 and the horizontal conveyer 213B of vertical conveyer 213A, the sectional area of grain path of the sectional area of deduction relay axis 242 is set as than the sectional area of the grain path behind 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, the degree of freedom that moves with respect to the grain of case 241 is in succession improved, make and do not stop up from the vertical fortune fortune 213A of mechanism to the grain handing-over of horizontal conveyer 213B and carry out swimmingly.From be fixed on the above-mentioned vertical conveyer 213A the upper end in succession the 241a of case section until the tote box 238 of horizontal conveyer 213B and set up hydraulic cylinder 245, by the expanding-contracting action of this hydraulic cylinder 245, horizontal conveyer 213B is driven up and down in set scope around above-mentioned transverse axis heart Q and is swung.

As shown in figure 25, the above-mentioned of bottom that is fixed on cereal box 208 in binding transports on the case 214, electro-motor 246 with reductor is installed, and, exported and the pinion 247 of positive and negative ground rotary actuation by its deceleration, with rim gear wheel 248 engagements on the tote box 235 that is packed in vertical conveyer 213A flange shapely, by the rotating action of electro-motor 246, grain transports device 213 integral body and is driven in rotation around vertical fulcrum P.Utilize in this wise grain to transport the rotation of device 213 and swinging up and down of horizontal conveyer 213B, the position of rotation of outlet 240 and height and position are moved, can at random change the grain drain position.

Then, illustrate to the drive structure of the screw rod of the above-mentioned end 210 of the primary shaft that transports device 213 as the above-mentioned grain of driving.

Such as Figure 29～shown in Figure 32, on the above-mentioned support plate 215 that the front lower of cereal box 208 possesses, be fixed with the carriage 250 of leading section of the fulcrum 210a of bearing supporting end screw rod 210, link input magazine 251 at the front surface of this carriage 250.In input magazine 251, be equipped with the input bevel gear 252 that links with above-mentioned fulcrum 210a and with the input bevel gear 253 of its engagement, the power shaft 254 that links with input bevel gear 253 side in the body projects.

Above-mentioned carriage 250 and input magazine 251 make the involutory binding of bight 250a, 251a, and in the space that forms between bight 250a, 251a, the core shift cam 256 that bearing 255 is installed in periphery is fixed on the fulcrum 210a of end screw rod 210 by outer build-in.The above-mentioned rotating fulcrum 212 that flows down guided plate 211 is outstanding to the place ahead of support plate 215, and the motion arm 257 that links with its jag engages with the bearing 255 of above-mentioned core shift cam 256 via slotted hole 258 up and down.According to this formation, the fulcrum 210a of end screw rod 210 is driven in rotation and 256 rotations of core shift cam, the motion arm 257 that engages with this core shift cam 256 is with corresponding to the amplitude of the core shift amount of core shift cam 256 and reciprocally swinging, flow down guided plate 211 and in set angle, driven by reciprocally swinging, thereby store that grain in container arch formation can not occur and flow down to the active region of end screw rod 210.

At cereal box 208 be configured on the organism frame 202 between the above-mentioned engine 204 in its place ahead, vertically be provided with bearing bracket 260, engine power is passed to and rotates the freely input belt wheel 261 in the horizontal axle center of mounting support on this bearing bracket 260.

Shown in the kinematic scheme of Figure 21, laterally carrying in the above-mentioned engine 204 that is equipped with, possess the outstanding main output shaft 262 in body side and drive the output shaft 263 of usefulness to the outstanding slave of body foreign side, crawler travel device 201, extract section 203 and sheller unit 207 by the power drive that obtains from main output shaft 262.Possesses 3 output pulley 264 at outside output shaft 263, the driving-belt 265 that water pump 266, cooling fan of engine 267, the generator 268 of radiator cooling usefulness is wound onto on this output pulley 264 drives, and the other driving-belt 269 that is wound on the above-mentioned output pulley 264 is wound onto on the above-mentioned input belt wheel 261.In addition, though not shown, other the driving-belt of can also reeling on above-mentioned output pulley 264 can drive the compressor of the cooling medium compression usefulness of the aircondition in the machine that is equipped in the passenger cabin specification.

As described above, intermediate propeller shaft 271 can along axis direction slidably spline be embedded in the center of the above-mentioned input belt wheel 261 that bears engine power.Intermediate propeller shaft 271, with the above-mentioned power shaft 254 of support on above-mentioned input magazine 251 with the involutory configuration in core ground, and the spring 272 that intermediate propeller shaft 271 is installed by outer embedding is subject to the application of force of sliding to power shaft 254.Intermediate propeller shaft 271 and power shaft 254, interlock links via engagement type clutch 273 at its involutory opposed position.

Above-mentioned clutch 273, comprise the clutch components 274 of the boss-shaped that links the top ends that is fixed on intermediate propeller shaft 271 and the engaging part 275 that is consisted of by the spring catch of squeezing into perforation in the top ends periphery of power shaft 254, clutch components 274 outer being embedded on the top ends of power shaft 254, thereby as shown in figure 29, engaging part 275 engagement of power shaft 254 snaps in the engaging recessed part 276 to the end diagonal position that is formed on clutch components 274, thus, carry out transmission of power from from middle power transmission shaft 271 to power shaft 254.

If cereal box 208 reclaims the position to the maintenance position rotary moving from grain, then as shown in figure 30, accompany with the movement to horizontal foreign side of power shaft 254, engaging part 275 is extracted from clutch components 274, removes the binding of intermediate propeller shaft 271 and power shaft 254.Opposite; if cereal box 208 reclaims the position rotation and returns from maintenance position to original grain; then accompany with the movement to horizontal interior side of power shaft 254, engaging part 275 engages with clutch components 274 from axis direction, and intermediate propeller shaft 271 and power shaft 254 automatically interlock link.Cereal box 208 reclaims the position and rotates when returning from maintenance position to grain; the rotatable phase of the engaging recessed part 276 of the clutch components 274 that stops the rotation and the engaging part 275 of power shaft 254 is offset sometimes; in this case; engaging part 275 butts are pressed the external end edge of clutch components 274, intermediate propeller shaft 271 overcome spring 272 and in the body side slide and retreat.Then, ato unit 204 and middle rotating shaft 271 begin rotation, when then the engaging recessed part 276 of clutch components 274 moves to the phase place of engaging part 275, middle rotating shaft 271 application of forces are slided and clutch 273 connections, and rotating shaft 271 and power shaft 254 automatically become the state that interlock links in the middle of making.

Such as Figure 33～shown in Figure 35, the direction A/F w of above-mentioned engaging recessed part 276 is set to about the several times of external diameter of engaging part 275, and the 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 the engaging part 275 of engaging recessed part 276, form the interior expansion shape that enters towards the rotary actuation direction.The easily engaging by engaging recessed part 276 and engaging part 275 are nipped, and avoid in advance clutch components 274 and intermediate propeller shaft 271 since the thrust that large driving counter-force etc. occur and together backboard change position make and the situation that engages easy disengaging of engaging part 275.

Claims (12)

1. the grain recoverer of a combine drives structure; about side by side configuration sheller unit (207) and cereal box (208); and on the front side of above-mentioned cereal box (208), laterally dispose engine (204); leading section to the end screw rod (210) of above-mentioned cereal box (208) transmits engine power; it is characterized by

Screw rod of the above-mentioned end (210) is provided in the outer end of the inside of above-mentioned cereal box (208), project output shaft (263) from above-mentioned engine (204) to body to horizontal foreign side, and laterally support has intermediate propeller shaft (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 intermediate propeller shaft (271), and interlock links the body outside left of above-mentioned intermediate propeller shaft (271) and the leading section of screw rod of the above-mentioned end (210).

2. the grain recoverer of combine as claimed in claim 1 drives structure; it is characterized in that; be equipped with screw rod of the above-mentioned end (210); so that with respect to be positioned at the horizontal outermost fore-and-aft direction frame parts of body along the body fore-and-aft direction from the organism frame section of the above-mentioned cereal box of lower side bearing (208), the axle core of screw rod of the above-mentioned end (210) is positioned at the body lateral outer side.

3. the grain recoverer of combine as claimed in claim 2 drives structure; it is characterized in that the bottom of the body lateral outer side of above-mentioned cereal box (208) is supported on above-mentioned fore-and-aft direction frame parts in the position lower than the upper end of above-mentioned fore-and-aft direction frame parts.

4. the grain recoverer of combine as claimed in claim 2 drives structure, it is characterized in that, forms lower narrow (208e) in the bottom of the body lateral outer side of above-mentioned cereal box (208),

From the horizontal wide center of above-mentioned cereal box (208) more to the bottom of horizontal foreign side's skew ground configuration above-mentioned lower narrow (208e), so that screw rod of the above-mentioned end (210) is positioned at than the organism frame of combine more in the outer part.

5. the grain recoverer such as each described combine of claim 1-4 drives structure; it is characterized in that; above-mentioned cereal box (208) constitutes and can rotate around vertical fulcrum (P) at rear, and is provided with the clutch (273) that takes off along body horizontal direction card along above-mentioned intermediate propeller shaft (271) and screw rod of the above-mentioned end (210) side.

6. the grain recoverer of combine as claimed in claim 5 drives structure, it is characterized in that, is provided with the spring (272) of above-mentioned intermediate propeller shaft (271) to the body lateral outer side direction slip application of force.

7. the grain recoverer of combine as claimed in claim 5 drives structure; it is characterized in that; be equipped with threshing grain at the rear of above-mentioned cereal box (208) and transport device (213); above-mentioned threshing grain transports device (213) and will be transported outside machine by the grain that screw rod of the above-mentioned end (210) is sent

Above-mentioned threshing grain transports the vertical conveyer (213A) that device (213) has the screw that is connected with the lower end, back of above-mentioned cereal box (208),

The screw rod axle center of above-mentioned vertical conveyer (213A) and above-mentioned vertical fulcrum (P) are with the configuration of core ground, and above-mentioned threshing grain transports device (213) integral body and constitutes and can rotate with above-mentioned cereal box (208).

8. the grain recoverer of combine as claimed in claim 7 drives structure, it is characterized in that, link in the rear end, bottom of above-mentioned cereal box (208) fulcrum (210a) that supporting screw rod of the above-mentioned end (210) is arranged rearward end transport case (214),

Support (202a) arranges to the horizontal foreign side of body is outstanding from the organism frame of combine, and the above-mentioned lower end boss portion (214a) that transports case (214) is chimeric being bearing on this support (202a) rotationally, and above-mentioned cereal box (208) can be supported rotatably around above-mentioned vertical fulcrum (P).

9. the grain recoverer such as each described combine of claim 1-4 drives structure; it is characterized in that; front surface at above-mentioned cereal box (208) has support plate (215); the bottom mounting of this support plate (215) is bearing on the upper surface of organism frame section; make above-mentioned cereal box (208) be supported on organism frame (202)

Be linked to above-mentioned support plate (215) for the input magazine (251) of screw rod of the above-mentioned end (210) transmission of power of above-mentioned intermediate propeller shaft (271).

10. the grain recoverer of combine as claimed in claim 9 drives structure; it is characterized in that; in above-mentioned input magazine (251); be equipped with the output bevel gear (252) that links with the fulcrum (210a) of screw rod of the above-mentioned end (210) and with the input bevel gear (253) of above-mentioned output bevel gear (252) engagement

The power shaft (254) that links with above-mentioned input bevel gear (253) just projects in body, and above-mentioned power shaft (254) links via clutch (273) interlock with above-mentioned intermediate propeller shaft (271).

11. the grain recoverer of combine as claimed in claim 9 drives structure; it is characterized in that; on above-mentioned support plate (215); be fixed with the carriage (250) of the leading section of the fulcrum (210a) that bearing supports screw rod of the above-mentioned end (210), link above-mentioned input magazine (251) at the front surface of this carriage (250).

12. the grain recoverer of combine as claimed in claim 11 drives structure; it is characterized in that; in the space that between above-mentioned carriage (250) and above-mentioned input magazine (251), forms; the core shift cam (256) that bearing (255) is installed in periphery is fixed on by outer build-in on the fulcrum (210a) of screw rod of the above-mentioned end (210)

Along the top of screw rod of the above-mentioned end (210), via rotating fulcrum (212) swingingly support have that cross sectional shape forms chevron flow down guided plate (211),

Above-mentioned rotating fulcrum (212) is outstanding to the place ahead of above-mentioned support plate (215), and the motion arm (257) that links with the jag of above-mentioned rotating fulcrum (212) engages with the above-mentioned bearing (255) of above-mentioned core shift cam (256) via slotted hole (258) up and down.

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