CN100411933C - Working vehicle - Google Patents
Working vehicle Download PDFInfo
- Publication number
- CN100411933C CN100411933C CNB2005100527129A CN200510052712A CN100411933C CN 100411933 C CN100411933 C CN 100411933C CN B2005100527129 A CNB2005100527129 A CN B2005100527129A CN 200510052712 A CN200510052712 A CN 200510052712A CN 100411933 C CN100411933 C CN 100411933C
- Authority
- CN
- China
- Prior art keywords
- mentioned
- power
- transfer clutch
- running gear
- operating area
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D11/00—Steering non-deflectable wheels; Steering endless tracks or the like
- B62D11/02—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides
- B62D11/06—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
- B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
- B62D1/12—Hand levers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2300/00—Purposes or special features of road vehicle drive control systems
- B60Y2300/02—Control of vehicle driving stability
Abstract
A working machine capable of smoothly steering a farm working machine has a pair of right and left crawler type running devices (1R, 1L), and a operation section (7) with a single steering means (42), and having a plurality of operation zones for leading the driving state of the running devices to be different from the single steering means neutral position (n) to each right-and-left rotation direction, wherein the operation haul cycle of one operation zone on each rotation direction are set larger than that of other operation zone. It can easily avoid oversteering by leading the second operation zone to have larger range when rotating.
Description
The application divides an application, and the denomination of invention of female case is the steering hardware of working rig, and the applying date of female case is March 29 calendar year 2001, and the application number of female case is 01112170.X.
Technical field
The present invention relates to have the cterpillar drive of pair of right and left working rig (such as, combination machine, rice transplanter etc.).
Background technology
In the past, as above-mentioned working rig, for example disclosed form in the flat 7-47973 document of TOHKEMY is arranged.Here the working rig of Ti Chuing is provided with the side power-transfer clutch respectively on the cterpillar drive of pair of right and left, and this working rig comprises slow rotary drive mechanism, this mechanism's offside power-transfer clutch is in one of them running gear of released state to the direction identical with the direction of action of another running gear that is not in released state, drive with low speed, realize slowly rotation (soft turn) less than this responsiveness.This working rig also comprises as rotary drive mechanism rapidly, and the offside power-transfer clutch is in the stop mechanism that one of them running gear of released state is braked.In addition, the rotation rapidly that is in braking mode of running gear that rotation is inboard is called spot turn (pivot turn).
In this working rig, steering control and side power-transfer clutch, slowly rotary drive mechanism, and stop mechanism are bonded assemblys in the following manner.At first, if steering control is operated from center position one side's to about deflection the 1st operating area, then with one of them the side disengaging of clutch of running gear, if then continue to operate, then, make the side power-transfer clutch be in the running gear deceleration of released state by slow rotary drive mechanism to the 2nd operating area, then, if continue to operate to the 3rd operating area, then by stop mechanism, the offside power-transfer clutch is in the running gear of released state and brakes.
In above-mentioned existing working rig, along with the increase of the operational ton of steering control, its verticity strengthens gradually, can carry out and the corresponding body rotation of steering operation amount, and operability is good.
But, when the rotary mode from the 1st operating area is transformed into the rotary mode (slowly rotary mode) of the 2nd operating area, the side clutch gear that constitutes the side power-transfer clutch is from the further conversion of declutched position, from shaft core direction and side gear engagement, thereby switch to the deceleration state quickly.Thus, produce side clutch gear and side gear ingear and impact or engagement sound, and in the body rotation, be attended by lighter impact.
Summary of the invention
The present invention be directed to such situation and propose, its main purpose is to provide a kind of working rig, and it can carry out and the rotation of the corresponding body of steering operation amount, and can carry out accurately smoothly that body turns to.And the 2nd operating area that adopts usually when rotating by making is bigger scope, prevents oversteer (rotation rapidly) easily.
To achieve these goals, working rig of the present invention is characterised in that technical scheme 1 described structure.Promptly, a kind of working rig, the cterpillar drive that possesses pair of right and left, with manoeuvre portion with mono-steering control, be formed with the 1st operating area successively from the center position of above-mentioned mono-steering control, the 2nd operating area, and the 3rd operating area, described the 1st operating area only slowly rotates by the driving of the running gear outside the rotation, described the 2nd operating area carries out the driving that speed is lower than the running gear in the rotation outside to rotating inboard running gear, slowly rotate, described the 3rd operating area is braked rotating inboard running gear, rotate rapidly, wherein, the operational stroke of above-mentioned the 2nd operating area is set greater than each operational stroke of above-mentioned the 1st operating area and above-mentioned the 3rd operating area.
Preferably, in the driving system of each running gear, be provided with the side power-transfer clutch, in above-mentioned the 1st operating area, disconnect and the inboard cooresponding side power-transfer clutch of running gear of rotation, only slowly rotate by the driving of the running gear outside the rotation, in above-mentioned the 2nd operating area, the inboard running gear of the open circuited rotation of offside power-transfer clutch carries out the driving that speed is lower than the running gear in the not open circuited rotation of the side power-transfer clutch outside, slowly rotate, in above-mentioned the 3rd operating area, the inboard running gear of the open circuited rotation of offside power-transfer clutch is braked, and rotates rapidly.
In addition, preferably, the deceleration of the running gear of the rotation inboard in above-mentioned the 2nd operating area is to add the multi-plate power-transfer clutch that hydraulic pressure is switched on operation via passing through in the driving system that is arranged on each running gear to carry out, and above-mentioned hydraulic pressure is that the operational ton of above-mentioned steering control is big more then high more.
Preferably, on above-mentioned manoeuvre portion, also be provided with the difference of potential instrument, be connected, detect the operating position of this steering control with above-mentioned steering control, the control lever of above-mentioned difference of potential instrument is stressed in the mode that is connected to from the side on the action component with above-mentioned steering control interlock.
According to said structure, by with steering control from center position towards about a side operate, at first with a side side disengaging of clutch, the running gear of side disengaging of clutch one side is in free state.At this moment, by the low torque transmission mechanism, low torque is passed to the running gear that the side power-transfer clutch is in released state one side.Therefore, can be not as before, after with the side disengaging of clutch, one side's running gear is just at once because of the anxious situation of stopping of walking load, the low torque propulsive effort of the side of body by accepting the low torque propulsive effort running gear and side power-transfer clutch be not in the opposing party who separates running gear propulsive effort difference poor, i.e. the responsiveness of two running gears and slowly rotate.
In addition, if then steering control is operated largely along equidirectional, then the side power-transfer clutch running gear that is in released state is connected with transmission device with rotation linkedly, the running gear that the side power-transfer clutch is in released state is decelerated driving, braking, or inversion driving, body rotates reliably by maintaining speed driven poorly left and right sides running gear.
In this occasion, the single rotary mode that drives that is in released state from the side power-transfer clutch is undertaken by rotating with clutch engagement to the switching of the two rotary modes that drive with velocity contrast (slowly rotary mode).At this moment, owing to have slidably low torque transmission mechanism, compare with engagement type power-transfer clutch, above-mentioned switching is successfully carried out under shock-free situation.
In addition, because steering control is being turned back to center position, when recovering straightaway, low torque still passes to the running gear that the side power-transfer clutch is in released state, even so under the side power-transfer clutch is engagement type situation, still carry out the engagement under the very little state of the velocity contrast of drive side and slave end.
Therefore, can carry out and the corresponding body rotation of steering operation amount, and can be in the transmission of torque of not separating in the running gear of released state midway at the side power-transfer clutch, can not have to impact, meticulous body smoothly turns to, and can form better operability.
Also have, after the body rotation, when recovering straightaway, still can expect the effect of level and smooth side clutch engagement.
Have, best above-mentioned low torque transmission mechanism is arranged at above-mentioned rotation with in the power-transfer clutch again.For example, by steering control is operated towards right-hand from center position, at first with the side disengaging of clutch on right side.In this occasion, being in the not rotation in the left side of released state at the side power-transfer clutch uses in the power-transfer clutch, the low torque transmission mechanism effect in left side, the part of the power of the running gear on the left of supplying with is given the rotation power-transfer clutch in left side by the low torque transmission mechanism back transfer in left side.
Here, since about rotation all connect linkedly mutually with any one running gear in the relative left and right sides of drive side of power-transfer clutch with coordination, so in the manner described above the rotation of giving the left side of the low torque transmission mechanism back transfer by the left side with the power of power-transfer clutch extend be passed to the right side rotation with in the power-transfer clutch, the power of this extension transmission passes to the running gear that power-transfer clutch is in the right side of released state by the rotation that is arranged on the right side with the low torque transmission mechanism on the power-transfer clutch.
Therefore, can not be created in behind the side disengaging of clutch, one side's running gear is just at once because of the anxious situation of stopping of walking load, the difference of the low torque propulsive effort of the side of body by accepting the low torque propulsive effort running gear and the propulsive effort of the running gear that the side power-transfer clutch is in unsegregated the opposing party and rotation lentamente.
So, being in the supply side power-transfer clutch not, the power of the running gear of released state one side passes through rotation power-transfer clutch and setting low torque transmission mechanism thereon, extend and pass to the running gear that the side power-transfer clutch breaks away from a side, thus, the extension transmission path of low torque power adopts the original driving system that is provided with, can be under situation simple in structure, the function of performance technical scheme 1 described invention, the square profit in the practicality is higher.
If in said structure, then as mentioned above, when engaging rotation with power-transfer clutch, be favourable for the single rotary mode that drives that is in separation from the side power-transfer clutch switches to the rotary modes of the poor two drivings that maintain speed.That is, be many plates friction-type by making this rotation power-transfer clutch, to compare with engagement type power-transfer clutch, above-mentioned switching is successfully carried out under shock-free situation.
In addition, carry out low torque transmission in power-transfer clutch in the corresponding rotation of running gear that is in above-mentioned the opposing party of released state not (the rotation outside) with the side power-transfer clutch by spring, use side gear with the part of the power of the corresponding side clutch gear of power-transfer clutch from turning to this rotation, by transmission shaft, pass to the corresponding rotation power-transfer clutch of running gear round with an above-mentioned side (rotation is inboard).Then, this circuitous power passes to the side clutch gear that is positioned at declutched position by the lighter frictional transmission by spring, and consequently, the inboard running gear of rotation is accepted the transmission of power of low torque.So the cterpillar drive that is in a side (rotation inboard) of released state at the side power-transfer clutch is being accepted in the transmission of power of the low torque that obtains from the power of the running gear of engage side (the rotation outside), the offside power-transfer clutch carries out lock out operation.Thus, can be at the side disengaging of clutch, cut off the transmission of active force after, the situation that running gear just stops because of the walking load has at once fully relaxed the impact that the separating action with the side power-transfer clutch produces.
In addition, in supply,, when a side side power-transfer clutch carries out separating action, also pressure oil is not supplied with the rotation power-transfer clutch with a side side clutch gear gear shift by pressure oil.After this, the part of the pressure oil of supply side power-transfer clutch is by the throttling circuit portion, supply with the rotation power-transfer clutch at leisure, rotation is carried out the clutch engagement action lentamente with power-transfer clutch, the running gear that the side power-transfer clutch is in a side of released state is connected with transmission device with rotation linkedly, carries out deceleration, braking, or inversion driving, body by the difference that maintains speed drives about running gear and rotate reliably.
So the rotation after the action of side disengaging of clutch is successfully carried out with the clutch engagement action of power-transfer clutch, can realize further that clutch on-off impacts very little body smoothly and turns to.
With reference to accompanying drawing and during the description below reading, will appreciate that other feature structure, action effect of the present invention.
Description of drawings
Fig. 1 is a combination machine single-piece right side view;
Fig. 2 is the front elevation of expression walking with the drive mechanism of gearbox body;
Fig. 3 is the longitudinal profile front elevation of the first half of the above-mentioned gearbox body of expression;
Fig. 4 is the longitudinal profile front elevation of the lower part of the above-mentioned gearbox body of expression;
Fig. 5 is the enlarged elevation front elevation of side power-transfer clutch periphery;
Fig. 6 is the lateral plan of the operating structure of vice speed-changing mechanism;
Fig. 7 is the longitudinal profile front elevation of gearshift that secondary speed-changing mechanism is operated;
Fig. 8 switches to secondary speed-changing mechanism for expression the longitudinal profile front elevation of the main portion of lower-speed state;
Fig. 9 switches to secondary speed-changing mechanism for expression the longitudinal profile front elevation of the main portion of middling speed state;
Figure 10 switches to secondary speed-changing mechanism for expression the longitudinal profile front elevation of the main portion of neutral condition;
Figure 11 switches to secondary speed-changing mechanism for expression the longitudinal profile front elevation of the main portion of fast state;
Figure 12 turns to the hydraulic circuit of usefulness and the constructional drawing of control system;
Figure 13 is the front elevation of steering operation portion;
Figure 14 is the lateral plan of steering operation portion;
Figure 15 turns to the lateral plan of using control part for expression;
Figure 16 turns to the longitudinal profile lateral plan of the periphery of transfer valve for expression;
Figure 17 represents to turn to the front elevation of the operating portion of transfer valve;
Figure 18 is the longitudinal profile lateral plan of the periphery of mode switch valve and adjustable relief valve.
The specific embodiment
Below with reference to the accompanying drawings, embodiments of the invention are described.Below, as an example of working rig, be that example is described with combination machine as reaper.
Fig. 1 is the right side view of combination machine.The structure of this combination machine is, has pair of right and left crawler-mounted running gear 1L, and the front portion of the traveling machine body 20 of 1R is connected with cutting pre-processing portion 3 in liftable mode, threshing apparatus 4 is set, grain case 5, driving engine 6, manoeuvre portion 7 etc. on body.
According to Fig. 2, Fig. 3 and Fig. 4 are to above line walking apparatus 1L below, and the drive mechanism of 1R is described, and still, the description of the left and right directions in the explanation is based on the left and right directions of body, and the left and right directions from these figure that the front is seen is in opposite relation.
The transmission of power of above-mentioned driving engine 6 is given the hydrostatic formula continuously variable unit of putting as the main transformer quick-mounting of the switching of advancing before and after can carrying out (HST) 8, and its speed change outputting power passes to gearbox body 9.The power of input gearbox body 9 is passing through gear G1, and after G2 passed to the 1st 10, by gear G3, G4 passed to secondary speed-changing mechanism 11.In addition, from the 1st 10 power that outputs to outside the casing, only turn power passes to above-mentioned cutting pre-processing portion 3 by free-wheel clutch OC.In addition, above-mentioned hydrostatic formula continuously variable unit 8 is by being arranged at main shift lever 29 operations in the manoeuvre portion 7.
Above-mentioned secondary speed-changing mechanism 11 carries out 3 grades gear change in the constant-mesh mode, its structure is: will be installed in the slack running fit mode at ordinary times on the 2nd 12 than minor diameter gear G5, intermediate diameters gear G6, than gear wheel in large diameter G7 and the gear G8 that is fixed on the 3rd 13, G9, G10 engagement, with 2 sliding sleeve S1 that are arranged on above-mentioned the 2nd 12, S2 moves, and adopt 3 groups of constant mesh gear centerings any one group, carries out from the 2nd 12 to the 3rd 13 speed change transmission.
Promptly, as Fig. 6, shown in 7, above-mentioned sliding sleeve S1, S2 engage respectively and are supported on a pair of shifting fork 15a, on the 15b, this is to shifting fork 15a, and 15b possesses along horizontal supporting in gearbox body in-to-in bolster on 14 gearshifts 15 that slide, along with the slide displacement of this gearshift 15, can be to two sliding sleeve S1, S2 carries out gear-change operation along equidirectional simultaneously.In addition, be provided with the motion arm 16a that engages with above-mentioned gearshift 15 at the front end that is installed in the variable speed operation axle 16 in the gearbox body 9 in front and back, the edge mode of passing, by the secondary shifter bar 30 that is arranged in the manoeuvre portion 7 is operated, rotate variable speed operation axle 16, carry out the operation that gearshift 15 horizontally slips thus.
Here, above-mentioned sliding sleeve S1 is in the whole zone of shift range, by spline and the 2nd 12 directly engagement, and above-mentioned sliding sleeve S2 can be in the hub portion of gear G6, be embedded in the spline axle collar 17 on the 2nd 12 outward by spline, and move in the scope of the hub portion of gear G7, in the following manner, realize 3 grades speed change.
When gearshift 15 is positioned at low speed " L " position, as shown in Figure 8, sliding sleeve S1 is in the 2nd 12 scope and the hub portion engagement of gear G5, sliding sleeve S2 is in the state on the hub portion that only outer embedding is supported on gear G6, the 2nd 12 power is by sliding sleeve S1, gear G5, G8 passes to the 3rd 13 with low speed.
When gearshift 15 is positioned at middling speed " M " position, as shown in Figure 9, sliding sleeve S1 only is supported on the 2nd 12, sliding sleeve S2 is in the state of the outer embedding interlock of hub portion of the scope of the spline axle collar 17 and gear G6, the 2nd 12 power is by the spline axle collar 17, sliding sleeve S2, gear G6, G9 passes to the 3rd 13 with middling speed.
In addition, when gearshift 15 was positioned at neutrality " N " position, as shown in figure 10, sliding sleeve S1 only was supported on the 2nd 12, and sliding sleeve S2 is in only outer embedding and is supported on state on the spline axle collar 17, cuts off the transmission of power from the 2nd 12 to the 3rd 13.In addition, when gearshift 15 is positioned at high speed " H " position, as shown in figure 11, sliding sleeve S1 only is supported on the 2nd 12, and sliding sleeve S2 is in the state of the outer embedding interlock of hub portion of the scope of the spline axle collar 17 and gear G7, and the 2nd 12 power is by the spline axle collar 17, sliding sleeve S2, gear G7, G10, at high speed pass to the 3rd 13.
In addition, as shown in Figure 7, above-mentioned switching mechanism 15 can be passed through ball detent 18, remain on the low speed " L " of using speed as the results of the paddy bar that stands upside down, as the results of standard middling speed " M " with speed, neutral " N ", and as the position of moving with the high speed " H " of speed.
Pass to the gear G9 of above-mentioned the 3rd 13 power by the centre in the manner described above and pass to after the 4th 19 the sun gear G11, by about side power- transfer clutch 20L, 20R, axletree gear 21L, 21R, and axletree 22L, running gear 1L about 22R passes to, 1R.
As shown in Figure 4, above-mentioned side power- transfer clutch 20L, 20R constitutes in the following manner, that is: will with the 4th 19 loosening chimeric and make constant-mesh in axletree gear 21L, the side clutch gear 23L on the 21R, the 23R gear shift, realize that from the center internal tooth of side and above-mentioned sun gear G11 engagement throws off, make thus from sun gear G11 that the transmission of power of 22R is interrupted and carries out to axletree 22L, with above-mentioned side clutch gear 23L, the mechanism that 23R switches constitutes in the following manner.
Above-mentioned the 4th 19 by the middle part be larger-diameter band stage portion the axle form, and side clutch gear 23L, 23R has the 4th 19 smaller diameter portion and is embedded in the internal diameter that has stage portion on the 4th 19 outside than large-diameter portion, forms oil pocket g, h between the stage portion.In addition, by spring 24L, 24R slides towards sun gear G11 one side and setovers at ordinary times, remain on clutch position, by being arranged in the 4th 19 in-to-in oil circuit a, b, to oil pocket g, h supply pressure oil, each side clutch gear 23L, 23R overcomes spring 24L, 24R, gear shift is then thrown off with sun gear G11 to limit position, keeps the disengaging of clutch state.In addition, if side clutch gear 23L, the 23R gear shift is to declutched position, and then pressure oil is supplied with the above-mentioned oil circuit a of usefulness, b with pass the 4th 19 in-to-in oil circuit d and be communicated with.
Also have, above-mentioned side clutch gear 23L, 23R arrive after the declutched position of throwing off with the interlock of sun gear G11, can be by multi-plate rotation power- transfer clutch 90L, 90R uses side gear 25L with the turning to of two-end part that is installed in the slack running fit mode the 4th 19, and 25R connects.
As shown in Figure 5, above-mentioned rotation power-transfer clutch 90L, the structure of 90R is, can becoming integrally rotated mode and side clutch gear 23L, the larger-diameter clutch outer member 91L of 23R bonded assembly, piston 92L is installed in chimeric mode in the inside of 91R, 92R uses side gear 25L from turning to simultaneously, the 93L of multiple spline hub portion that 25R extends, 93R and above-mentioned clutch outer member 91L between the 91R, are provided with in groups friction plate 94L in stacked mode, 94R, usually, by spring 95L, 95R, with piston 92L, 92R puts towards disengaging of clutch one lateral deviation, to clutch outer member 91L, 91R in-to-in oil pocket i, j supply pressure oil overcomes spring 95L, 95R and make piston 92L, 92R produces displacement, crimping friction plate 94L in groups, 94R, thus, carry out using side gear 25L from turning to, 25R is to side clutch gear 23L, the transmission of power of 23R.
, make rotation use power-transfer clutch 90L here, the piston 92L of 90R, the oil pocket i of 92R action, j is communicated with oil circuit k by passing the gear in-to-in, g and makes side clutch gear 23L, the oil pocket g of 23R action, and h is communicated with, be communicated with oil circuit k at this, among the g, be provided with throttling circuit portion p, q.
In addition, power-transfer clutch 90L is used in rotation, and the inside of 90R constitutes in the following manner, that is: with piston 92L, and the spring that 92R pushes towards clutch engagement one side (example of low torque transmission mechanism) 100L, 100R is assemblied in a plurality of positions of piston ring Zhou Fangxiang.This spring 100L, 100R are moderately gently with piston 92L, and 92R is pressed against the frictional transmission position, thus all the time with the rotary power of low torque from side power-transfer clutch 20L, turning to of 20R uses side gear 25L, 25R to pass to rotation power-transfer clutch 90L, the clutch outer member 91L of 90R, 91R.
Also have, above-mentioned turning to used side gear 25L, 25R and the gear 27L that is fixed in the two-end part of the 5th (being equivalent to the low torque transmission shaft) 26, the 27R interlock, mesh with the gear G12 that is connected in above-mentioned sun gear G11 sidepiece with slack running fit mode and the 5th 26 chimeric gear G13 simultaneously, realize the deceleration interlock than minor diameter.
Between said gear G13 and the 5th 26, be provided with the slowly multi-plate power-transfer clutch C of rotation (soft turn) effect.At ordinary times under the effect of the interior spring of establishing 31, make piston 32 fallback recoveries, this power-transfer clutch C remains on the disengaging of clutch state, by by the in-to-in oil circuit c supply pressure oil that passes the 5th 26, piston 32 overcomes spring 31 and displacement, thereby this power-transfer clutch C switches to the clutch engagement state.
Have, an end of the 5th 26 is supported on by bearing on the side cover 33 on the right flank that is installed in gearbox body 9 again, on this side cover 33, has been provided with the multi-plate stop mechanism B of spot turn (pivot turn) effect.In this stop mechanism B, the piston 34 of ring-type applies by hydraulic pressure, side's turnover in the casing relatively, and the spring of establishing in overcoming 36 is pushed pressing plate 35 and is made its displacement, thus, adds brake drag effect to the 5th 26.In stop mechanism B, with the releasing that applies of this hydraulic pressure, make pressing plate 35 recover to retreat by the interior spring of establishing 36, will brake releasing thus.Above-mentioned piston 34 is assemblied in the hydraulic cylinder 37 on the lateral surface that is installed in side cover 33.
Figure 12 is above-mentioned side power- transfer clutch 20L, 20R, and power-transfer clutch 90L is used in rotation, 90R, power-transfer clutch C, and hydraulic circuit diagram that turns to usefulness and control system figure that stop mechanism B is operated.In the figure, V1 represents to be used to select a ground to above-mentioned side power-transfer clutch 20L, the side clutch gear 23L of 20R, 23R carries out the transfer valve that turns to of gear-change operation, the screw actuator SL1 in the outside by being arranged at gearbox body 9, select neutral, and 3 positive and negative positions.V2 represents any one supply pressure oil in above-mentioned power-transfer clutch C or stop mechanism B selectively, switch the mode switch valve of rotary mode, usually, it is biased to towards the pressure oil of power-transfer clutch C and supplies with the position, the screw actuator SL2 in the outside by gearbox body 9 is set switches to this valve towards the pressure oil of stop mechanism B and supplies with the position.
In addition, V3 among Figure 12 represents and forms above-mentioned the 4th 19 in-to-in oil circuit d bonded assembly sequence valve, its operating pressure is set at following pressure, even side power-transfer clutch 20L, the side clutch gear 23L of 20R, the 23R gear shift is to declutched position, pressure with spring 24 maintenance balances, in addition, the downstream of this sequence valve V3 is connected with adjustable relief valve V4, be communicated with the gearbox body 9 as the action fuel tank simultaneously, and be connected with the initial side of above-mentioned mode switch valve V2 from the oil circuit e of branch between sequence valve V3 and the adjustable relief valve V4.
To the above-mentioned screw actuator SL1 that turns to transfer valve V1 to operate, and the screw actuator SL2 that mode switch valve V2 is operated by controller 43 be arranged at manoeuvre portion 7 in control desk 41 in deflecting bar (example of steering control) 42 be electrically connected, above-mentioned adjustable relief valve V4 mechanically is connected with deflecting bar 42 simultaneously.
As Figure 13, shown in Figure 14, on the carriage 44 of the top right side that is installed on handle platform 41 (from operator's one side), but according to front and back to around fulcrum x free rotation mode, bolster 45 is installed with connecting, and at the supporting point part 46 that is connected in these bolster 45 rear ends, according to the mode that can laterally swing around fulcrum y above-mentioned deflecting bar 42 is installed, deflecting bar 42 constitutes according to the mode that can carry out cross swing.In addition, be equipped with the 1st motion arm 47 (example of action component) that makes the L-shaped bending of rod member and form from above-mentioned supporting point part 46, simultaneously from be equipped with the 2nd motion arm 48 of sheet material near the front end of above-mentioned bolster 45, the 1st motion arm 47 in the following manner be installed on handle platform 41 on difference of potential instrument 49 be connected, detect the operating position of deflecting bar 42 by electronic mode.
Promptly, the control lever 49a of above-mentioned difference of potential instrument 49 is according in the mode that contacts with above-mentioned the 1st motion arm 47 from the side at ordinary times, under interior effect of establishing spring, setover along the right-hand revolution among Figure 13, even from center position n, along about any direction situation that the 1st motion arm 47 is operated under, when keeping in touch, control lever 49a rotates with the 1st motion arm 47, thus the output as difference of potential instrument 49 of the operating position of deflecting bar 42 is changed, detect continuously, this detection signal is input in the controller 43.
In addition, above-mentioned the 2nd control lever 48 is connected on the overflow metal wool 50 that above-mentioned adjustable relief valve V4 is operated in the following manner.That is, on above-mentioned bolster 45, in the slack running fit mode 51,52, two movement arms 51,52 of a pair of movement arm are set and depend on to mutual approaching direction by torque spring 53, the mode that is arranged at the set pin 54 on the carriage 44 according to clamping contacts supporting.In addition, the movable end of a movement arm 51 therein connects the end of the outside metal wool 50a that is supported with overflow metal wool 50, and at the movable end of another movement arm 52, connects the end of the inboard metal wool 50b that is supported with overflow metal wool 50.In addition, be arranged between two movement arms 51,52 by the operative pin 48a of deflecting bar 42 front and back to the movable end setting of the 2nd motion arm of swinging around fulcrum x 48.
If employing said structure, for example, in Figure 13, when to deflecting bar 42 from center position n, towards dextrorotation direction (left among the figure) when carrying out swinging operation, then make the 2nd motion arm 48 along the swing of the anticlockwise direction among the figure, operative pin 48a makes one of them movement arm 51 contact swing in the counterclockwise direction.Because this moment, another movement arm 52 contacts with set pin 54, and its swing is in the counterclockwise direction stoped, so relatively pull out the inner layer metal line 50b of metal wool 50 from outside metal wool 50a.In addition, in contrast, if carry out swinging operation from center position n along left hand direction to deflecting bar 42, then make the 2nd motion arm 48 along the swing of the clockwise direction among the figure, operative pin 48a makes another movement arm 52 contact swings along clockwise direction.At this moment, a side movement arm 51 stops its swing along clockwise direction by contacting with set pin 54, pulls out the inboard metal wool 50b of metal wool 50 thus from outside metal wool 50a.Promptly, no matter be deflecting bar 42 to be carried out swinging operation from center position n any one direction towards left hand direction or dextrorotation direction, corresponding its operational ton, all the inner layer metal line 50b in the metal wool 50 is pulled out operation, the amount of pulling out of this metal wool is big more, and the operating pressure of above-mentioned adjustable relief valve V4 is high more.
Turn to transfer valve V1 and sequence valve V3 to be assemblied in the above-mentioned hydraulic cylinder 37, above-mentioned mode switch valve V2 and adjustable relief valve V4 are assemblied on the side cover 33, be interconnected by the in-to-in oil circuit that is formed at hydraulic cylinder 37 and side cover 33, form hydraulic circuit shown in Figure 11.
Pair turn to transfer valve V1 according to Figure 15～18 below, mode switch valve V2, and the operating structure of adjustable relief valve V4 is described.
Shown in Figure 15～17, the above-mentioned transfer valve V1 that turns to constitutes in the following manner, that is: can engage with motion arm 63 by bolster 62 along the plunger 61 that fore-and-aft direction is installed on the top of hydraulic cylinder 37 slidably from exterior oscillations, realize slide, above-mentioned screw actuator SL1 is connected on the bar 64 of the outer end that is installed in bolster 62 in the interlock mode.
If the employing said structure, when deflecting bar 42 was positioned at center position n, screw actuator SL1 was in non-power status, and plunger 61 remains on center position by recovering spring 65, and the pressure oil of supplying with from pumping hole P turns back to gearbox body 9 through discharging stream.
If deflecting bar 42 is operated along left hand direction, then this situation is detected by difference of potential instrument 49, SL1 pushes driving to spiral tube, along the left among Figure 15 to plunger 61 is carried out slide, pass through oil circuit a by the pressure oil of supplying with from pumping hole P, supply with left-handed with side power-transfer clutch 20L.
If deflecting bar 42 is operated along the dextrorotation direction, then this situation is detected by difference of potential instrument 49, to the screw actuator SL1 driving that stretches, along the right among Figure 15 plunger 61 is carried out slide, the pressure oil of supplying with from pumping hole P passes through oil circuit b, supplies with the side power-transfer clutch 20R that dextrorotation is used.
As Fig. 4, shown in Figure 180, above-mentioned mode switch valve V2 constitutes in the following manner, that is: push by contacting according to the plunger 66 on the top that can be installed on side cover 33 from 68 pairs of the motion arms of exterior oscillations along the mode that fore-and-aft direction slides by bolster 67, overcome spring 69 and carry out slide, above-mentioned screw actuator SL2 is connected with the bar 70 of outer end on being installed in bolster in the interlock mode.
If adopt this structure, when screw actuator SL2 was in non-power status, plunger 66 was positioned at position shown in Figure 180, and the oil circuit e in the downstream of sequence valve V3 is communicated with the oil circuit c that extends to power-transfer clutch C.In addition, drive screw actuator SL2 if switch on, its action that stretches, then bar 70 is along the swing of the anticlockwise direction among Figure 18, and plunger 66 overcomes spring 69 and switches, and above-mentioned oil circuit e is communicated with the oil circuit f that extends to stop mechanism B.
As Fig. 4 and shown in Figure 8, above-mentioned adjustable relief valve V4 constitutes in the following manner, that is: comprise being assemblied in poppet valve 71 on the top of side cover 33 movably along fore-and-aft direction; Poppet valve 71 biasings are pressed against on the valve seat 72, cut off above-mentioned oil circuit e and the spring that is communicated with 73 of discharging stream D; Support the spring reception part 74 of these spring 73 rear ends, by motion arm 76, by pushing this spring reception part 74 from motion arm 76 contacts of exterior oscillations by the tubular bolster 75 that outer embedding is installed on the above-mentioned bolster 67, make its slide displacement, thereby the scalable oil pressure relief, the inboard metal wool 50b in the above-mentioned release metal wool 50 is connected in the interlock mode with bar 77 on being installed on bolster 75 outer ends.In addition, above-mentioned bar 77 is under the effect of torque spring 78, along making motion arm 76 deviate from the direction swing biasing of spring reception part 74, as shown in the figure, in biasing swing boundary line, motion arm 76 contacts with the inner face of side cover 33, and the oil pressure relief among the adjustable relief valve V4 of this moment is substantially zero.In addition, as previously described, if deflecting bar 42 is swung, the inboard metal wool 50b that discharges in the metal wool 50 is carried out stretched operation, motion arm 76 is swung along the anticlockwise direction among Figure 18, spring reception part 74 is pressed into, it is subjected to displacement, and the oscillating quantity of deflecting bar 42 increases, and the metal wool amount of tension strengthens, thereupon, the oil pressure relief of adjustable relief valve V4 increases gradually.
Also have, the lifting of above-mentioned cutting pre-processing portion 3 is carried out in the swing of the above-mentioned deflecting bar 42 by can carrying out the cross operation.That is, shown in Figure 14 as Figure 13, be provided with the sensor 81 that constitutes by the difference of potential instrument of the swing that detects deflecting bar 42 or switch etc. about on the extended line of horizontal fulcrum y; With the torque spring 81 of deflecting bar 42 towards the center position n biasing of front and back swaying direction, not shown driving lifting mechanism in sensor 81 and the cutting pre-processing portion 3 connects into, if detect the place ahead that deflecting bar 42 swings to center position n by sensor 81, then make above-mentioned cutting pre-processing portion 3 carry out down maneuver, swing to the rear if detect this bar, then make above-mentioned cutting pre-processing portion 3 carry out vertical motion by sensor 81.
Have again, label 83 expression among Fig. 2 is according to the drg of stopping of being provided with of the mode on above-mentioned the 3rd 13 end of acting on and parking usefulness, by being arranged at the operation of entering into of the stretcher 84 in the manoeuvre portion 7, not shown master clutch is carried out lock out operation, and above-mentioned drg 83 is carried out brake operating, and this master clutch is arranged at the driving system from driving engine 6 to hydrostatic formula continuously variable unit 8.In addition, by pedal 84 cards are only remained in the position of entering into, then can start parking brake.
Working rig of the present invention constitutes in the manner described above, below handling maneuver is described.
When above-mentioned deflecting bar 42 is positioned at center position n, side power- transfer clutch 20L, 20R all is in engagement state, with about cterpillar drive 1L, 1R is according to identical speed drive, body is directly walked.
If with deflecting bar 42 from the center position n side the direction to the left and right, for example right-hand the 1st operating area Rc swing, then detect this situation by difference of potential instrument 49, energising drives screw actuator SL1, to turn to transfer valve V1 to switch to the dextrorotation position, pressure oil supplies to oil pocket h by oil circuit b, makes side clutch gear 23R move to declutched position, disconnects the side power-transfer clutch 20R on right side.Thus, only the cterpillar drive 1R on right side is in idling conditions, and by only driving the cterpillar drive 1L in left side, body slowly rotates towards right.
In this occasion, the rotation that is in the left side (the rotation outside) of non-separation state at side power-transfer clutch 23L is used among the power-transfer clutch 90L, carry out low torque transmission by spring 100L, the part of the power of side clutch gear 23L passed to turn to use side gear 25L, by gear 27L, the 5th 26, gear 27R, and turn to and use side gear 25R, extend the rotation power-transfer clutch 90R that passes to right side (rotation is inboard).In addition, this changes power under the effect of the frictional transmission gently that passes through spring 100R, passes to the side clutch gear 23R that is positioned at declutched position, and the cterpillar drive 1R on right side accepts the transmission of power of low torque.Therefore, accept at the cterpillar drive 1R on right side in the transmission of power of the low torque that obtains from the power of left row walking apparatus 1L, offside power-transfer clutch 23R carries out lock out operation, can not separate at side power-transfer clutch 23R, when the transmission of active force cuts off, cterpillar drive 1R stops under the effect of walking load immediately fully, and the impact of the separating action generation of following side power-transfer clutch 23R is slowed down.
In addition, if the side power-transfer clutch 20R on right side is separated, after this, pressure oil among the oil pocket h is also supplied with the oil pocket j of the rotation on right side with power-transfer clutch 90R by being communicated with oil circuit g, rotation is in engagement state with power-transfer clutch 90R, but because during deflecting bar 42 was in the 1st operating area Rc, the operating pressure of adjustable relief valve V4 was also very low, can not carry out joint action so be in the power-transfer clutch C that receives the pressure oil condition of supplying by mode switch valve V2, not drive to turn to and use side gear 25R.So,, rotation is carried out bonding operation and body turns to irrelevant with power-transfer clutch 90R at this state.
If deflecting bar 42 is operated the 2nd operating area Rs, then the oil pressure relief of adjustable relief valve V4 is the value that surpasses the operating pressure of sequence valve V3, higher pressure oil is supplied with power-transfer clutch C by oil circuit e and oil circuit c, make power-transfer clutch C carry out bonding operation, driven at low speed according to the rules turns to uses side gear 25R.Therefore, this turns to the low speed power with side gear 25R to pass to the side power-transfer clutch 20R that is positioned at declutched position by rotation with power-transfer clutch 90R, under the lower-speed state that according to the rules ratio slows down, drive the cterpillar drive 1R on right side, according to left and right sides cterpillar drive 1R, the actuating speed of 1L is poor, and body rotates lentamente towards right reliably.
In this occasion, operate the 2nd operating area Rs if will be positioned at the deflecting bar 42 of center position n quickly, then as mentioned above, right side side power-transfer clutch 20R is separated, and power-transfer clutch C carries out joint action apace, the rotation on right side is also carried out the clutch engagement action with power-transfer clutch 90R, but because the pressure oil in the oil pocket h among the side power-transfer clutch 20R of right side is by having the connection oil circuit g of throttling circuit portion, supply with the oil pocket j of rotation at leisure, so rotation is successfully carried out with the clutch engagement of power-transfer clutch 90R is slow in one's movements with the larger sectional area among the power-transfer clutch 90R.Therefore, pass to the power that turns to side gear 25R by power-transfer clutch C and do not pass to side clutch gear 23R with having impact, the cterpillar drive 1R on right side successfully is in the deceleration state.
Here, because the pressure oil that imposes on above-mentioned power-transfer clutch C is subjected to the restriction of adjustable relief valve V4, so the deflecting bar 42 in the 2nd operating area Rs is the closer to center position n one side, the hydraulic pressure that puts on the power-transfer clutch C is low more, more little by power-transfer clutch C torque transmitted, the 2nd operating area Rs in-to-in deflecting bar 42 leaves center position n more, and the hydraulic pressure that puts on the power-transfer clutch C is high more, and the torque that passes to the cterpillar drive 1R on right side by power-transfer clutch C increases gradually.Finally, power-transfer clutch C full engagement drives the cterpillar drive 1R on right side under the lower-speed state that according to the rules ratio slows down.
If make deflecting bar 42 exceed the 2nd operating area Rs, it is operated the 3rd operating area SL2, then detect this situation by difference of potential instrument 49, switch on and driving screw actuator SL2, V2 switches to the mode switch valve, and oil circuit e is communicated with oil circuit f, pressure oil the supply system actuation mechanism B, oil circuit c is communicated with discharge stream D simultaneously, and power-transfer clutch C is separated.In this occasion, by deflecting bar 42 is operated largely, because above-mentioned oil pressure relief increases, so by stop mechanism B, with the 5th 26 braking, under the state that will stop with the cterpillar drive 1R braking on interlock mode and the 5th 26 bonded assembly right side, only drive the cterpillar drive 1L in left side, body rotates (pivot turn) rapidly towards right.
In addition, if deflecting bar 42 is turned back to center position n from the body steering state, the side power-transfer clutch 23R that then is in the right side of released state carries out joint action, return to straight moving condition once more, but because in this occasion, the right side rotation is carried out the low torque transmission with power-transfer clutch 90R, the side clutch gear 23R on right side rotates slightly, so occasion that the velocity contrast between sun gear G11 and the side clutch gear 23R has stopped less than side clutch gear 23R, do not causing under the engagement condition of poor, side clutch gear 23R successfully meshes with sun gear G11 once more.
Also have, though do not describe, but also identical in the occasion of deflecting bar 42 being operated with above-mentioned situation towards left hand direction, at the 1st operating area Lc, only carry out anticlockwise slowly with the side power-transfer clutch 20L separation in left side, at the 2nd operating area Ls, carry out power-transfer clutch C bonding operation, with the anticlockwise of the cterpillar drive 1L deceleration in left side, in addition, at the 3rd operating area Lb, carry out the rotation rapidly that the cterpillar drive 1L to the left side brakes towards left.
(other embodiment)
The all right following form of the present invention is implemented.
(1) as low torque being passed to side clutch gear 23L, the low torque transmission mechanism of 23R, except in the manner described above, with the rotation power-transfer clutch 90L that passes to about power that the side power-transfer clutch do not separate the running gear of a side passes through, 90R extends beyond the transmission, also can be by power-transfer clutch slidably etc., the transmission of power that will provide from the driving system of the special use of independent setting becomes low torque power.
(2) in the above-described embodiments, the deflecting bar 42 that can swing still, also can be used the steering tiller that is rotated operation as steering control as steering control.
(3) also can be by a pair of range fork from the outside to above-mentioned side power-transfer clutch 20L, the side clutch gear 23L among the 20R, 23R carries out the structure of gear-change operation.In this occasion, also can operate this range fork by the hydraulic actuating cylinder of peripheral hardware respectively.
(4) also can be with the 3rd operating area Lb, Rb is as the state in the direction of action counter-rotating of the running gear that makes clutch engagement side (rotation the outside), and the offside power-transfer clutch is in the pattern of spot turn rapidly (spin turn mode) that the running gear of a side of released state (rotation is inboard) carries out deceleration to be implemented.。
(5) also can be with the 3rd operating area Lb, Rb is in the drg rotary mode that the running gear of a side of released state is braked as above-mentioned such offside power-transfer clutch, at the 3rd operating area Lb, the more lateral of Rb is provided with reverse deceleration side power-transfer clutch and is in the 4th operating area of the pattern of spot turn rapidly of the running gear of a side of released state simultaneously.
Claims (4)
1. working rig, cterpillar drive (the 1R that possesses pair of right and left, 1L), with the manoeuvre portion with mono-steering control (42) (7), be formed with the 1st operating area (Rc successively from the center position (n) of above-mentioned mono-steering control, Lc), the 2nd operating area (Rs, Ls), and the 3rd operating area (Rb, Lb), described the 1st operating area only slowly rotates by the driving of the running gear outside the rotation, described the 2nd operating area carries out the driving that speed is lower than the running gear in the rotation outside to rotating inboard running gear, slowly rotate, described the 3rd operating area is braked rotating inboard running gear, rotate rapidly, it is characterized in that
The operational stroke of above-mentioned the 2nd operating area (Rs, Ls) is set greater than each operational stroke of above-mentioned the 1st operating area (Rc, Lc) and above-mentioned the 3rd operating area (Rb, Lb).
2. working rig according to claim 1 is characterized in that,
In the driving system of each running gear, be provided with side power-transfer clutch (20R, 20L),
In above-mentioned the 1st operating area (Rc, Lc), disconnection and the inboard cooresponding side power-transfer clutch of running gear of rotation are only slowly rotated by the driving of the running gear outside the rotation,
In above-mentioned the 2nd operating area (Rs, Ls), the inboard running gear of the open circuited rotation of offside power-transfer clutch carries out the driving that speed is lower than the running gear in the not open circuited rotation of the side power-transfer clutch outside, slowly rotate,
In above-mentioned the 3rd operating area (Rb, Lb), the inboard running gear of the open circuited rotation of offside power-transfer clutch is braked, and rotates rapidly.
3. working rig according to claim 2, it is characterized in that, the deceleration of the running gear of the rotation inboard in above-mentioned the 2nd operating area is to add the multi-plate power-transfer clutch (C) that hydraulic pressure is switched on operation via passing through in the driving system that is arranged on each running gear to carry out, and above-mentioned hydraulic pressure is that the operational ton of above-mentioned steering control (42) is big more then high more.
4. according to each described working rig in the claim 1～3, it is characterized in that,
On above-mentioned manoeuvre portion (7), also be provided with difference of potential instrument (49), be connected, detect the operating position of this steering control with above-mentioned steering control (42),
The control lever (49a) of above-mentioned difference of potential instrument (49) is stressed in the mode that is connected to from the side on the action component (47) that links with above-mentioned steering control (42).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000091472A JP3541159B2 (en) | 2000-03-29 | 2000-03-29 | Agricultural work equipment steering device |
| JP91472/2000 | 2000-03-29 | ||
| JP91472/00 | 2000-03-29 |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB01112170XA Division CN1200835C (en) | 2000-03-29 | 2001-03-29 | Steering device for working vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1660639A CN1660639A (en) | 2005-08-31 |
| CN100411933C true CN100411933C (en) | 2008-08-20 |
Family
ID=18606930
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB01112170XA Expired - Fee Related CN1200835C (en) | 2000-03-29 | 2001-03-29 | Steering device for working vehicle |
| CNB2005100527129A Expired - Fee Related CN100411933C (en) | 2000-03-29 | 2001-03-29 | Working vehicle |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB01112170XA Expired - Fee Related CN1200835C (en) | 2000-03-29 | 2001-03-29 | Steering device for working vehicle |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP3541159B2 (en) |
| KR (1) | KR100373584B1 (en) |
| CN (2) | CN1200835C (en) |
Families Citing this family (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102678836B (en) * | 2012-05-23 | 2015-02-18 | 南通市广益机电有限责任公司 | Transmission case for electrically controlling vehicle to walk |
| CN103935399B (en) * | 2014-04-01 | 2016-08-03 | 江苏云马农机制造有限公司 | A kind of steering braking device |
| CN106413379B (en) * | 2014-05-19 | 2019-03-26 | 洋马株式会社 | Combine harvester |
| CN104290813B (en) * | 2014-10-29 | 2016-11-09 | 东莞市优势达机械科技有限公司 | Individual soldier's tank adjustable engine |
| WO2016117543A1 (en) * | 2015-01-19 | 2016-07-28 | 株式会社神崎高級工機製作所 | Vehicle steering system |
| CN104541752B (en) * | 2015-01-20 | 2016-05-18 | 延寿县闪电农业装备有限公司 | Full hydraulic drive track combine |
| CN105065614A (en) * | 2015-06-25 | 2015-11-18 | 南通黄海药械有限公司 | Hydraulic-drive stepless speed changing gearbox for crawler-type spraying machine |
| JP6616274B2 (en) * | 2016-12-07 | 2019-12-04 | ヤンマー株式会社 | Work vehicle |
| JP6861024B2 (en) * | 2016-12-21 | 2021-04-21 | 株式会社クボタ | Harvester |
| CN106828601B (en) * | 2017-02-13 | 2019-03-26 | 北京理工大学 | A kind of unmanned vehicle steering by clutch machine steering system |
| CN106741160B (en) * | 2017-02-13 | 2019-07-09 | 北京理工大学 | A kind of working method of unmanned vehicle steering by clutch machine steering system |
| CN109654215B (en) * | 2018-11-30 | 2023-10-13 | 浙江云洲科技有限公司 | Flexible steering gearbox hydraulic control system |
| CN110406374B (en) * | 2019-08-05 | 2021-11-16 | 山推工程机械股份有限公司 | Main clutch and steering clutch linkage device for bulldozer and bulldozer |
| KR102232762B1 (en) * | 2020-11-19 | 2021-03-26 | (주)한성티앤아이 | Automatic transmission for high place operation car with spin turn function |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0747973A (en) * | 1993-08-05 | 1995-02-21 | Kubota Corp | Turning operation structure of working vehicle |
| JPH08256542A (en) * | 1995-03-23 | 1996-10-08 | Kubota Corp | Rice transplanter |
| JPH08337126A (en) * | 1996-07-24 | 1996-12-24 | Kubota Corp | Front wheel drive control device for four-wheel drive type agricultural tractor |
| CN1038808C (en) * | 1992-06-29 | 1998-06-24 | 株式会社久保田 | Operational unit of clutch of moving paddy field machine |
-
2000
- 2000-03-29 JP JP2000091472A patent/JP3541159B2/en not_active Expired - Fee Related
-
2001
- 2001-02-28 KR KR10-2001-0010265A patent/KR100373584B1/en active IP Right Grant
- 2001-03-29 CN CNB01112170XA patent/CN1200835C/en not_active Expired - Fee Related
- 2001-03-29 CN CNB2005100527129A patent/CN100411933C/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1038808C (en) * | 1992-06-29 | 1998-06-24 | 株式会社久保田 | Operational unit of clutch of moving paddy field machine |
| JPH0747973A (en) * | 1993-08-05 | 1995-02-21 | Kubota Corp | Turning operation structure of working vehicle |
| JPH08256542A (en) * | 1995-03-23 | 1996-10-08 | Kubota Corp | Rice transplanter |
| JPH08337126A (en) * | 1996-07-24 | 1996-12-24 | Kubota Corp | Front wheel drive control device for four-wheel drive type agricultural tractor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1200835C (en) | 2005-05-11 |
| CN1660639A (en) | 2005-08-31 |
| JP2001278100A (en) | 2001-10-10 |
| KR20010093649A (en) | 2001-10-29 |
| CN1319521A (en) | 2001-10-31 |
| JP3541159B2 (en) | 2004-07-07 |
| KR100373584B1 (en) | 2003-02-26 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100411933C (en) | Working vehicle | |
| CN101959733A (en) | Traveling agricultural machine | |
| JP5833168B2 (en) | Gearbox for work vehicle | |
| JP5426731B2 (en) | Transmission device for work vehicle | |
| JP4474842B2 (en) | Work vehicle | |
| JP5592539B2 (en) | Transmission device for work vehicle | |
| JP3708389B2 (en) | Agricultural machinery steering device | |
| JP2001193835A (en) | Gear change mechanism of agricultural machine | |
| JP2000351386A5 (en) | ||
| JP5346456B2 (en) | Transmission device for work vehicle | |
| JP3268568B2 (en) | Steering control device for traveling vehicles | |
| JP3828529B2 (en) | Agricultural tractor | |
| JP2009058031A (en) | Work vehicle | |
| JP3583063B2 (en) | Agricultural work equipment steering device | |
| JP3828528B2 (en) | Agricultural tractor | |
| JP2005324791A (en) | Steering device of agricultural working machine | |
| JP2850708B2 (en) | Steering operation device such as combine | |
| JP3662157B2 (en) | Agricultural machinery steering device | |
| JP4070737B2 (en) | Combine steering device | |
| JP4889600B2 (en) | Transmission device for work vehicle | |
| JP2000350507A5 (en) | ||
| JP2000018375A (en) | Shift operation mechanism of working vehicle | |
| JP2007203985A (en) | Working vehicle | |
| JP3662547B2 (en) | Agricultural tractor travel drive device | |
| JPH0328572A (en) | Operation arrangement for vehicle transmission |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080820 Termination date: 20200329 |