CN1507768A - Riding-type working machine in paddy field - Google Patents

Abstract

The riding type paddy field working machine comprises: front wheels(2) supported by a front axle case(20); rear wheels(3) supported by a second axle case(30); a vertically movable elastic supporting unit(6) for independently suspending the respective front wheels; and a fluctuating supporting unit(7) for allowing the rear wheels to vertically fluctuate about a transverse axis.

Description

Ride-type paddy field machine

Technical field

The present invention relates to a kind of ride-type paddy field machine with the front-wheel that is supported on the front truck axle box and the ride-type rice transplanter that is supported in the trailing wheel on the back axle case etc.More particularly, the present invention relates to a kind of is the ride-type paddy field machine of characteristics with the wheel suspension structure.

Background technology

Typical example as ride-type paddy field machine, it is the wheel suspension structure of ride-type rice transplanter, known structure is that left and right sides front-wheel is when being bearing on the gearbox that is fixed on fore-body, left and right sides trailing wheel is bearing in (reference example such as Japanese Patent Application Laid-Open 2003-102215 communique) on the rear portion back axle case that is supported on rotationally on the fuselage afterbody, on the one hand, left and right sides front-wheel is bearing on the gearbox that is fixed on fore-body, on the other hand, trailing wheel axle respectively is supported on the rearward end of the casing that swings that stretches out backward from gearbox, and the displacement (reference example such as Japanese Patent Application Laid-Open 2003-81140 communique) up and down independently of left and right sides trailing wheel.

When the ride-type rice transplanter when the field high speed is walked, the fuselage swing and the vibration that are caused by the convex-concave of field become very fierce, occupant's mood worsens easily, great changes will take place also to make simultaneously the position of the rice shoot planting unit that is connected fuselage afterbody and attitude easily, even carry out automatic lifting control, can not fully corresponding deflection, the precise decreasing that can cause planting depth, thereby, to improving the speed of travel of planting in the practical operation certain limitation is arranged, be difficult to give full play to the ability of rice transplanter, the operation of planting efficiently.

Particularly, because it is very big to be positioned at the variation of the fuselage attitude that the trailing wheel of planting before the rice shoot device convex-concave place by field causes, the influence that the position and the attitude of rice shoot planting unit changed thereby wishes to improve suspension structure for rear wheel very greatly.

In the equipment shown in the Japanese Patent Application Laid-Open 2003-102215 communique, when front-wheel installation in the left and right sides is supported on the gear box that is fixed on fore-body, left and right sides trailing wheel is supported on the rear portion transmission case body (owing to be equivalent to back axle case of the present invention, being called the back axle case hereinafter) that is supported on rotationally on the fuselage afterbody.In the device of this form, left and right sides difference in height for the field of trailing wheel process, the function of suspension is given full play in the rotation of back axle case, can restrain inclination big about fuselage, but when left and right sides trailing wheel passed through the recess of field or protuberance simultaneously, the function of draft hitch did not play a role, fuselage afterbody or sinking significantly, or rise.In addition, be directly installed on the front-wheel on the fixing gear box, do not have the function of draft hitch certainly, front-wheel causes the variation of walking fuselage attitude along the convex-concave motion of field.

Relative therewith, in the equipment shown in the Japanese Patent Application Laid-Open 2003-81140 communique, on the one hand, left and right sides front-wheel is installed and is supported on the gear box that is fixed on fore-body, on the other hand, trailing wheel axle respectively is supported on the rearward end of the casing that swings that stretches out backward from gear box, can be independently the elastic bearing left and right sides, displacement ground trailing wheel up and down.In the device of this pattern, swing the independently draft hitch function of casing of utilization absorbs the left and right sides difference in height of the field of trailing wheel process effectively, when left and right sides trailing wheel passes through the recess of field or protuberance simultaneously, also can give full play to the function of draft hitch, can contain the significantly swing (pitching) of the fuselage of walking, still, because front-wheel does not have the function of draft hitch, when front-wheel passed through the convex-concave place of field, the attitude of fuselage changed, and had the leeway of improveing.

Summary of the invention

The present invention be directed to that the problems referred to above make, the purpose of this invention is to provide a kind of function of giving full play to the draft hitch of front-wheel and trailing wheel, can be on the field ride-type paddy field machine of walking at a high speed smoothly.

To achieve these goals, ride-type paddy field machine of the present invention is a kind of ride-type paddy field machine that comprises the front-wheel that is supported on the front truck axle box and be supported in the trailing wheel on the back axle case, it is characterized in that, also comprise: respectively above-mentioned front-wheel of independent suspension and the flexible supporting mechanism that can move up and down, make aforementioned trailing wheel with along the transverse axis center steering (Japanese: Heng Shaft core ま ゎ り) of fuselage left and right directions but the swing supporting mechanism of above-below direction swing.

If the employing said structure in front wheel side, relies on the telescopic action of flexible supporting mechanism, each front-wheel can be complied with the concavo-convex of field independently, thereby the attitude of containment fore-body changes.

In addition, in rear wheel-side, by means of the swing effect of the transverse axis center steering of swinging supporting mechanism's generation, trailing wheel effectively utilizes the casing length of back axle, more increased the sphere of action of the flexible bias pressure of this swing supporting mechanism, made trailing wheel can change the position up and down.That is to say, as only with the flexible flexible supporting mechanism that can move up and down and constitute of the above-below direction of straight line, the elastic force sphere of action of supporting device and the change amount of trailing wheel upper-lower position much at one, still, in contrast to this, the upper-lower position change amount of trailing wheel is bigger.

Thereby, in so big scope, do not act on even be used for the elastic force of swinging operation in the swing supporting mechanism, also can increase the variation of trailing wheel upper-lower position, make trailing wheel can comply with bigger concavo-convex variation better.

And, because swing supporting mechanism is the structure can swing along the transverse axis center steering of fuselage left and right directions, therefore, even swing, distance between transverse axis center and the back axle does not change yet, can pass through the transverse axis core, mechanically transmit the driving force to trailing wheel, this drive mechanism can form by simple parts.

In a preferred example, utilize above-mentioned swing supporting mechanism, respectively each trailing wheel of suspension independently.

If the employing said structure, the telescopic action of the flexible supporting mechanism of each front-wheel utilization is complied with the concavo-convex of field independently, and the attitude of containment fore-body changes.Each trailing wheel also utilizes the swing effect of swing supporting mechanism, complies with the concavo-convex of field independently, and the attitude of containment fuselage afterbody changes.

That is to say that because front and back wheel all adopts independent suspension frame unit, compare with the suspension mode of controlling trailing wheel rotationally with the height and position up and down that makes front-wheel is fixing, this mode can improve the concavo-convex compliance of wheel to field.

In addition, in rear wheel-side, because the PTO axle of corresponding rear workover rig is set, the back axle case makes its swing backwards, except having the effect that the height and position up and down that makes trailing wheel changes, also has by the swing of back axle case and avoids effect from the impact in the place ahead.

Under a preferred example, above-mentioned back axle case is designed to single casing, with each trailing wheel mounting support on this single casing.The transverse axis center of above-mentioned swinging mounting structure extends through the front end of the cramp bar that forwards extends from above-mentioned back axle case, with this transverse axis center as fulcrum, above-mentioned back axle case easy on and off swing and about can be connected with fascinating and be bearing on the walking fuselage.In above-mentioned flexible supporting mechanism, setting can be distinguished independent and first spring of displacement ground each front-wheel of elastic bearing up and down, in above-mentioned swing supporting mechanism, second spring of elastic bearing back axle case is set.

If employing said structure, for example when trailing wheel was made up of the pair of right and left trailing wheel, in case left and right sides trailing wheel is set foot on the protrusion and the recess of field simultaneously, the back axle case moved up and down abreast, each trailing wheel is equidirectional moving up and down simultaneously, the big front and back of containment walking fuselage fascinate (pitching).In addition, in case one-sided trailing wheel is set foot on the protrusion and the recess of field, back axle case left and right directions fascinates, and fascinates about the walking fuselage that containment left and right sides trailing wheel difference of height is brought (yaw).

In addition, the telescopic action of the flexible supporting mechanism of each front-wheel utilization is complied with the concavo-convex of field independently, and the attitude of containment fore-body changes.

Under a preferred example, be provided with the regulation device that laterally moves of the aforementioned back axle case of restriction.If employing said mechanism, for example when trailing wheel is made up of the pair of right and left trailing wheel, can realize following effect, just limit unnecessary laterally the moving of transmission case body and cramp bar, only can stipulate swing up and down and about fascinate, make left and right sides trailing wheel give full play to desirable suspension function really.

At this moment, in above-mentioned swing supporting mechanism, when the pair of right and left cramp bar is set, the draft hitch of elastic bearing back axle case is set, and above-mentioned regulation device preferably includes the transverse bar that is erected between back axle case or cramp bar and the vehicle body frame.If adopt this structure, add above-mentioned action effect, by the left and right sidesing post that keeps the compartment of terrain to be provided with, when can stablizing well supporting box, utilize a pair of bearing spring that keeps compartment of terrain, the left and right sides to be provided with, the supporting fuselage load relevant stably with left and right sides trailing wheel.

For example the real fair 7-50300 communique of Japanese kokai publication hei 7-99812 communique and Japan has been introduced other ride-type paddy field machine in the prior art.

In the ride-type paddy field machine that Japanese kokai publication hei 7-99812 communique is introduced, utilizing lifting control devices such as lifting linking member mechanism to when being arranged on seedling-planting device on the traveling machine body ground level is controlled, owing to make trailing wheel backswing around fulcrum of fuselage side in front and back, control is rolled, also control the left and right sides attitude of fuselage, therefore, keep horizontal attitude, Yi Bian plant operation Yi Bian control seedling-planting device.

In addition, in above-mentioned communique, also shown to replace this rolling control, compress spring (being equivalent to the 2nd spring of the present invention) carries left off hind wheel about utilization, and by lifting control, the technology of the combining structure of left and right sides independent suspension mode and left and right sides independent-lifting mode.

And in the real fair 7-50300 communique of above-mentioned communique and Japan, make following technology open, just in the front wheel side of fuselage of walking, can the above-below direction telescopic moving each front-wheel of the independent suspension left and right sides, ground, in case front-wheel falls into field convex-concave place, alleviating the fuselage that is caused tilts, the low phenomenon of craspedodrome is (in addition, in Japanese kokai publication hei 7-99812 communique, particularly with reference to paragraph 0008～0011, Fig. 1～5 and paragraph 0013～0015 and Fig. 8.In the real fair 7-50300 communique of Japan, with reference to the 3rd page and Fig. 7).

As mentioned above, freely constitute in the structure of trailing wheel rising and falling,, to be difficult to absorb fully at the convex-concave of field, cause easily fuselage about fascinate and up-down vibration, in addition,, cause the attitude confusion of planting seedlings of seedling-planting device in case the convex-concave degree increases.

Just, even left and right sides trailing wheel rises and falls, the convex-concave of field is not the camber of left and right symmetrically unanimity.Wheel falls into recess when a rear flank only, unless the opposite side trailing wheel raises synchronously equally, just can not avoid occurring fuselage inclination or above-below direction change in location.Thereby, cause low and passenger's mood deterioration by the craspedodrome that fuselage tilts and up-down vibration causes.

And, when described concavo-convex degree uniformity is big, worry that also the seedling-planting device that is supported on the walking fuselage is subjected to big influence, particularly, when fuselage afterbody reaches on the protuberance, the seedling-planting device at rear is lifted to the top above the controlled quentity controlled variable of apparatus for controlling of lifting, and it is very shallow to cause planting seedlings, and produces the improper state of floating seedling.

This improper in order to handle, open the spy of Japan and to have introduced a kind of above-mentioned fluctuating control mode that do not adopt in the flat 7-99812 communique, but make the draft hitch of all independent suspension modes of front and back wheel improve technology concavo-convex place compliance by employing.If adopt this prior art, have following problems.

In a word, if concavo-convex less,, can especially improve compliance to the concavo-convex place of field by adopting the draft hitch structure of independent suspension mode.But, usually in field concavo-convex, also have sizable jog.Thereby, this situation of imagination, if with the effective range of suspension frame structure set very big, under the almost indeclinable condition of fuselage weight self, correspondence is absorbed in big recess and rides big protuberance, must make the wheel height that bigger variation takes place, the telescopic variation amplitude is greatly enlarged, because the wheel height that the centre position of slinky spring maintains the standard, the elastic force of suspension frame structure is soft excessively, even the minimum concavo-convex stability of fuselage that also makes worsens, be not suitable for.

In order to avoid the above-mentioned situation that is not suitable for, the spy of Japan opens in the flat 7-99812 communique and has introduced a kind of situation, and the independent-lifting mode of the full wheel of the control of independent suspension mode and other lifting distinctively just makes up.Thereby, obtain not limit the improvement of compliance of concavo-convex size and two kinds of performances of fuselage stability.But, if adopt the combination of the suspension frame structure of this independent suspension mode and two kinds of forms of independent-lifting mode, be accompanied by integrally-built complicatedly, also increased cost.Adopt conduct very difficult corresponding to the mechanical transmission structure of the transmission form of the driving wheel of this Sulky rice transplanter.If adopt the spy of Japan to drive the hydraulic motor that flat 7-99812 communique is introduced, be subjected to considerable restraint in the design, improper.

In addition, in the scheme of the independent suspension front-wheel that the real fair 7-50300 communique of Japan is introduced, even can improve front-wheel corresponding to the concavo-convex compliance of field, can not expect the improvement of the compliance of rear wheel-side, be self-evident.

Thereby, in a kind of preferable example of ride-type paddy field machine according to the invention, utilize above-mentioned flexible supporting mechanism, allow that to prolonging direction stroke is little from the said reference height to the stroke ratio of allowing of shrinkage direction from the altitude datum of each front-wheel.

If employing said structure, front-wheel downwards allow ratio that amount of movement is set upward allow that amount of movement is big.Thereby, the current wheel when being absorbed in recess, the lean forward variation of attitude of easier certain containment fuselage.And flexible supporting mechanism leans forward and causes on shallow the planting more effectively suppressing fuselage, can be used as containment because of the shallow means that cause floating seedling of planting.

In a preferred example, according to above-mentioned swing supporting mechanism, to the lower side the stroke ratio of allowing allows that to uplifted side stroke is little from the said reference position from the reference position of above-mentioned trailing wheel.

If employing said structure, trailing wheel upward allow ratio that amount of movement is set downwards allow that amount of movement is big.Thereby when trailing wheel rode over protuberance, the attitude that easier certain containment fuselage tail rises changed.Thereby the effective travel of swing supporting mechanism is more effective on shallow the planting that inhibition fuselage tail liter causes, and can be used as containment because of the shallow means that cause that floating seedling takes place of planting.

In a preferred embodiment, above-mentioned flexible supporting mechanism comprises first spring that is made of the compression spring, and this first spring always is in confined state in whole spring compression travel gamut.

If the employing said structure in the gamut of the flexible stroke of flexible supporting structure, can make the start well of compression spring reaction.Thereby, have the advantage that better containment fuselage attitude changes.

In a preferred embodiment, above-mentioned swing supporting mechanism comprises second spring that is made of the compression spring, and the coefficient of elasticity of this second spring is littler than the coefficient of elasticity of above-mentioned first spring.

Usually the backgear ratio front-wheel is more near the apparatus for work (for example, the seedling-planting device in transplanting rice seedlings machine) of fuselage afterbody, because its amount of moving up and down is big to the influence of planting depth.In light of this situation, in carrying out the swing supporting mechanism that trailing wheel moves up and down, the coefficient of elasticity of first spring in the flexible supporting mechanism of the ratio front wheel side that the coefficient of elasticity of second spring is set is little.

Thereby, promptly be used in select big trailing wheel move up and down scope and with the pendulum angle scope of trailing wheel set very big, spring force changes the little ratio that just can realize its amount of movement.Thereby, when complying with the concavo-convex of field, when trailing wheel changes at bigger upper-lower position, make trailing wheel swing reposefully or move, can response well comply with.

With reference to accompanying drawing, read following explanation, will know the further feature structure of ride-type paddy field machine of the present invention and the action effect and the advantage of relevant structure.

Description of drawings

Fig. 1 is an all end view that meet the present invention's first example, and an example that has shown ride-type paddy field machine is the ride-type rice transplanter just;

Fig. 2 is all planes of rice transplanter shown in Figure 1;

Fig. 3 is the front view of the front wheel suspension structure of rice transplanter shown in Figure 1;

Fig. 4 is the plane of power train of the suspension structure for rear wheel of rice transplanter shown in Figure 1;

Fig. 5 is the end view of the suspension structure for rear wheel of rice transplanter shown in Figure 1;

Fig. 6 is the plan view that shows suspension structure for rear wheel shown in Figure 5;

Fig. 7 is the end view of other modified example that shows the front wheel suspension structure of rice transplanter shown in Figure 1;

Fig. 8 is the end view of another modified example of the front wheel suspension structure of rice transplanter shown in Figure 1;

Fig. 9 is the end view of other modified example of the suspension structure for rear wheel of rice transplanter shown in Figure 1;

Figure 10 is an all end view that meet the present invention's second example, and an example that has shown the ride-type paddy field machine that meets this example is the ride-type rice transplanter just;

Figure 11 is the end view of the suspension frame structure of front-wheel and trailing wheel in the rice transplanter shown in Figure 10;

Figure 12 is the plan view that shows suspension frame structure shown in Figure 11;

Figure 13 is the front view that shows front wheel suspension structure shown in Figure 11;

Figure 14 is the end view that shows suspension structure for rear wheel in the rice transplanter shown in Figure 10;

Figure 15 is the plan view that shows suspension structure for rear wheel shown in Figure 14;

Figure 16 is the front view that shows suspension structure for rear wheel shown in Figure 14;

Figure 17 is all plan views that show rice transplanter middle machine body guide frame shown in Figure 10;

Figure 18 is the expansion cross section that rear wheel drive is used the interior of back axle case in the demonstration rice transplanter shown in Figure 10;

Figure 19 is the cross section that rear wheel drive is used the key position of back axle case in the demonstration rice transplanter shown in Figure 10;

Figure 20 is the cross section that shows side clutch operating in the rice transplanter shown in Figure 10;

Figure 21 is an all end view that meet the present invention's the 3rd example, and an example that has shown the ride-type paddy field machine that meets this example is the ride-type rice transplanter just;

Figure 22 is the vertical view of having no progeny of left side clutch in the rice transplanter shown in Figure 21;

Figure 23 is the vertical view of having no progeny of right side clutch and brake in the rice transplanter shown in Figure 21;

Figure 24 is the diagrammatic plan view of homing guidance mechanism in the rice transplanter shown in Figure 21;

Figure 25 is the plan view of the key position of demonstration homing guidance shown in Figure 21 mechanism;

Figure 26 is oil hydraulic circuit figure in the rice transplanter shown in Figure 21;

Figure 27 is the view that shows side clutch operating characteristic in the rice transplanter shown in Figure 21.

The reference numeral explanation

1 walking fuselage, 2 front-wheels, 3 trailing wheels, 6 flexible supporting mechanisms, 7 swing supporting mechanisms 20; 110 front truck axle boxes, 30; 115 back axle casees; 60; 137 first springs 70; 164 second springs, 118 vehicle body frame, 151 supporting arms, 159 transverse bar L0 altitude datums (reference position), the flexible supporting mechanism of S1 shrinkage direction allow stroke, the flexible supporting mechanism of S2 prolonging direction allow stroke, S3 swing supporting mechanism upper side allow stroke, S4 swing supporting mechanism lower side allow stroke, X; A transverse axis center (axis of oscillation of swing supporting mechanism)

Embodiment

Hereinafter in conjunction with the accompanying drawings, the ride-type rice transplanter based on as an example of ride-type paddy field machine illustrates ride-type paddy field machine of the present invention.

(first example)

(integral body of ride-type paddy field machine constitutes)

Fig. 1 shows all end views of ride-type rice transplanter, and Fig. 2 shows all planes of ride-type rice transplanter.

Described ride-type rice transplanter by utilize the elevating lever of forming by quadric chain 41 connect 8 of plantations with seedling-planting device 4 and by carry 8 of fertilisings with fertilizer apparatus 5 adopt central authorities fixedly 8 of the plantations that constitute of fertilizer application mode with the ride-type rice transplanter, described elevating lever 41 is assembled in the ride-type with pair of right and left front-wheel 2 and pair of right and left trailing wheel 3 and walks on the rear portion of fuselage 1 and pass through the operation of oil cylinder 40 and lifting and swinging.

As illustrated in fig. 1 and 2, walking fuselage 1 is the four wheel drive type, just utilizes tape drive mechanism 11, static oil pressure endless gearing device (HST or the hydraulic drive of carrying on vehicle body frame 10; A kind of example of stepless speed change device) the 12 gear transmission device (not shown)s that are contained in will being sent to from the power of the engine E that carries in walking fuselage 1 front portion gear box 13 in will be sent to left and right sides front-wheel 2 with power from the walking of described gear transmission device by the interior left and right sides front truck axle box 20 interior front-wheel drives 21 that are contained in.For left and right sides rear wheel 3, first power transmission shaft 14 that will transmit by fore-and-aft direction from the power output of gearbox 13 and in the rear wheel drive devices 31 that are contained in the back axle case 30 be transferred to left and right sides rear wheel 3.

On walking fuselage 1, be provided with the manoeuvre portion lid 15 of mounted engine E in comprising, side disposed thereon handling maneuver left and right sides front-wheel 2 steering wheel 16, floor, equipped section 17 and operator's seat 18 etc. take operating portion.

As illustrated in fig. 1 and 2, seedling-planting device (a kind of example of apparatus for work) 4 comprises the walking that is accompanied by fuselage and the position of planting seedlings of garden face H is put in order in advance 5 whole ground plankers 42 on ground.In addition, be sent to box for feeding odd 44 with power by the 2nd power transmission shaft 43 from the operation of gearbox 13, be used to the distributed power of self-assembly casing 44, the seedling carrying base 45 of mounting 8 row seedlings is back and forth driven along left and right directions stroke according to the rules.Simultaneously, left and right directions 8 rotary growing bodies 46 be arrangeding in parallel of spacing according to the rules takes out the rice shoot of specified quantity at every turn and their is formed 8 and is planted on the field capablely from the lower end of seedling carrying base 45, in addition, the mounting table of rice shoot is purchased in symbol 9 expressions of fore-body.

Fertilizer apparatus 5 has following structure, the ditch device 47 of doing that is assembled on the whole ground planker 42 is accompanied by the walking of fuselage corresponding to each row formation fertilising groove of planting, 8 conveying mechanisms 50 utilize the operation power of gear box 13, the fertilizer of output specified quantity from fertilizer funnel 51, by the operation of electric fan 52, with the fertilizer of each conveying mechanism 50 output, by guiding flexible pipe 53, facing to making ditch device 47 pressurized delivered accordingly, fertilizer is embedded in the position, horizontal side of the rice shoot of planting in the field.

In this ride-type rice transplanter, the suspension frame structure that carries out the front and back wheel supporting has following structure.(based on the front wheel suspension structure of flexible supporting mechanism 6)

As mentioned below, this flexible supporting mechanism 6 has following structure, to give corresponding to front-wheel 2 to the first compression spring (a kind of example of first spring) 60 of down spring with at the front truck axle box 20 that allows the first compression telescopic spring mobile status lower support front-wheel 2, free along the vertical direction telescopic moving ground support front-wheel 2.

As shown in Figure 3, adorn on the front truck axle box 20 of front-wheel drive 21 in left and right sides front-wheel 2 is installed in, front-wheel 2 become be transmitted from front truck axle box 20 in the driving wheel of power of front driving device 21, utilize the steering tie rod 22 of the revolution operation that transmits described steering wheel 16, center on the axis Y in the king pin 23, in the predetermined angular scope, carry out steering operation.

Above-mentioned front-wheel drive 21 has following structure, the power output that transmits the gear box 13 of engine E power is sent to horizontal power transmission shaft 24 by differential attachment (figure is outer), utilize bevel gear 24a, 23a, described power be sent to the above-mentioned king pin 23 of double as above-below direction the axle on, utilization is set at the bevel gear 23b and the engagement that is set at the bevel gear 25a on the front axle 25 of the bottom of this above-below direction axle, transmits described power to front-wheel 2.

Front truck axle box 20 by the fixedly upper box body 20A of vehicle body frame 10 1 sides, the fixing lower part box 20B of front wheel side, between two casing 20A and 20B and with respect to upper box body 20A up and down the middle housing 20C of change location form.

Thereby the front axle 25 that is supported on the lower part box 20B can be supported up or down with respect to upper box body 20A in the lower-upper length scope of middle housing 20C, thereby front-wheel 2 can move up and down.

And, in front truck axle box 20, the first compression spring 60 that is made of helical spring adopts rolled state to be installed on the periphery of king pin 23, the upper end side of the first compression spring 60 abuts against the inside race of the bearing 20Aa that is used to install bevel gear 23a, it moves upward restricted, bevel gear 23a is fixedly mounted on the upper box body 20A by upper-lower position, the lower end side of the first compression spring 60 abuts against the thrust bearing 20Ca on the inner bottom part that is set at middle housing 20C, limit its downward motion, utilize middle housing 20C, apply downward elastic force to lower part box 20B.

In addition, the bevel gear 23b that is set on the lower end side of above-mentioned king pin 23 has following structure, just be positioned at the lower side of the bearing 20Ba that is fixed on the lower part box 20B, and be accompanied by moving up and down of lower part box 20B the upper-lower position of king pin 23 is fixed on the king pin 23 with changing, king pin 23 utilizes and is provided thereon distolateral stop component 23c regulation decline boundary.

The above-mentioned first compression spring 60 always is in confined state in the telescopic spring stroke four corner.Utilize this structure, in flexible stroke four corner, the elastic force effect of the first compression spring 60 is brought into play in reaction well.

Fig. 3 is presented in the fuselage that is under the normal operating condition and compresses this first compression spring 60 upward from the first altitude datum L0 (altitude datum that is equivalent to each front-wheel) that compresses the place, lower end of spring 60 in maximum is allowed stroke S1, the lower end of spring moves to maximum rising upper limit level face Lt (at this moment, the following end in contact of the upper end of lower part box 20B and upper box body 20A, the rising of lower part box 20B is in the state of being prevented).Just under this state, the following end in contact of the upper end of lower part box 20B and upper box body 20A is in the state that rises of preventing.On the contrary, maximum downwards allow stroke S2 be exactly the said reference height L0 and the first compression spring 60 the threshold level face Lb that descends to greatest extent (at this moment, the stopping element 23c of king pin upper end side is in the top position of upper box body 20A, with the supporting king pin 23 bearing 20Ab contact, be in decline by the prevention state) between distance.The first compression spring 60 always is in confined state in the gamut of described telescopic spring stroke.

As mentioned above, if L0 watches from altitude datum, since make to the lower side allow stroke ratio upward side allow the big (S1＜S2=just of stroke, with go up moving compare of containment according to front-wheel 2 risings, can contain following the moving that is absorbed in according to front-wheel 2 more energetically, owing to containing the shallow generation of planting the floating seedling that causes of being leaned forward and being caused by fuselage, so being provided with is in allowing stroke range, can apply flexibly effectively.(based on the rear wheel suspension mechanism of swing supporting mechanism 7)

Shown in Fig. 4～6, on the pair of right and left back axle case 30 of dress rear wheel drive device 31, the rear wheel drive device 31 corresponding in the back axle case 30 sent the power from above-mentioned first power transmission shaft 14 in each trailing wheel 3 of the left and right sides was installed in.

Utilize the horizontal drive shaft of rear wheel 32 that is connected with first power transmission shaft 14 and make and distinguish interrupted pair of right and left side clutch 33, carry out from the power transmission of wheel drive unit 31 backward of first power transmission shaft 14 from the power of the corresponding to the left and right rear wheel drive device 31 of drive shaft of rear wheel 32.The dress state was set in the rear portion back axle case 34 in this power transmitting mechanism adopted, the boss 30A of the base end side of left and right sides back axle case 30 is embedded in outward on the tubular bearing 34A of portion of the left and right end portions that is formed on rear portion back axle case 34, and is supported respectively with rotating relatively freely.

Be subjected to the influence of leaf spring 33a, above-mentioned side clutch 33 keeps the clutch on-state usually, the moving meter 33b that can carry out opening operation inserts and is embedded on the horizontal drive shaft of rear wheel 32, link with the steering operation of steering wheel 16, disconnect with going back to inboard trailing wheel 3 transmissions to above-mentioned moving meter 33b being linked to each other with the operating body 33c that operates in clutch disconnection side above predetermined angular.

The rear wheel drive device 31 that is set in the above-mentioned back axle case 30 constitutes by being separately positioned on above-mentioned drive shaft of rear wheel 32, back axle 36 and the gear train on the relay axis 37 between these two axles, transmits power by the wheeled reducing gear 35 of deceleration transmission left and right tooth in the corresponding trailing wheel 3 to back axle 36.

Back axle case 30 is rotated relatively freely the ground pivot and is propped up on the tubular bearing 34A of portion of the left and right end portions that is formed on rear portion back axle case 34, axis of pitch X around the fuselage left and right directions can freely swing, and is used to make the swing supporting mechanism 7 of back axle case 30 swings to have structure hereinafter described.

As illustrated in Figures 5 and 6, rear portion in vehicle body frame 10, one end of top bearing object 71 is fixed on the 10A of vertical wall portion that is installed on the lifting linking member 41, bottom bearing object 72 is installed on the back axle case 30, the second compression spring (a kind of example of second spring) 70 is installed between the distolateral and bottom bearing object 72 of the trip of top bearing object 71.The coefficient of elasticity of this second compression spring 70 is not had the coefficient of elasticity of the above-mentioned first compression spring 60 of fixed ratio little.

In Fig. 5 and 6, symbol 73 expressions are set at the core between top bearing object 71 and the bottom bearing object 72, in the deflection of the containment second compression spring 70, by making the distolateral axial region 71A of trip that is set at top bearing object 71 embed formed slotted hole 73A, determine the upper and lower bound of the pendulum angle scope of back axle case 30.

Fig. 5 has shown under the fuselage normal operating condition normal place in the flexible direction of the 2nd compression spring 70.From then on state upward the side maximum allow that stroke S3 is that the altitude datum L0 that shows in the drawings the 2nd compression spring 70 lower ends (be equivalent to the back axle case and then be equivalent to the reference position of trailing wheel) and its lower end position rise to the distance between the maximum upper limit horizontal plane Lt (at this moment, for example the 2nd coil spacing that compresses spring 70 is 0 state).Maximum downwards allows that stroke S4 is the distance between altitude datum L0 and the 2nd compression spring 70 maximum decline threshold level face Lb (at this moment, the upper end side of the slotted hole 73A of core 73 contacts with axial region 71A, prevents the state that descends).

As mentioned above, L0 watches from altitude datum, the ratio that stroke is set of allowing to upside is allowed the big (S3＞S4) just of stroke to downside, so be provided with, be absorbed in following moving the comparing that recess causes with containment trailing wheel 3, going up of can containing more energetically that trailing wheel 3 rides that protuberance causes is moving, can contain that fuselage afterbody rises shallow the planting that cause and the generation of the floating seedling that causes can be applied flexibly effectively and be allowed stroke.

As shown in Figure 6, leaving the above-mentioned vertical wall 10A of portion owing to the trip of top bearing object 71 is distolateral is formed, the distolateral axial region 71A of trip that is set at top bearing object 71 utilizes 2 supports that are fixed that separate, the above-mentioned core 73 and the second compression spring 70 are installed in axial region 71A on the horizontal lateral direction jag of fuselage, by removing the latch 74 of axial region 71A, the second compression spring 70 can be taken off with collar 75.

In addition, by the axial region 72A that takes off described bottom bearing object 72, the latch 76 or the split circlip 79 of its each end, also axial region 72A can be taken off from the bottom bearing object 72 that is fixed on the back axle case 30, thereby also core 73 can be pulled down.Thereby, can change the core 73 second compression spring 70 different with the elasticity fixed number that is used to set different pendulum angle bounds with elastic force, the swing start scope of back axle case 30 is done different settings with the swing performance.

In addition, the coefficient of elasticity of the above-mentioned first compression spring 60 of the ratio that is set of coefficient of elasticity of the best second compression spring 70 is little.

(the change example of first example)

(1) also can in above-mentioned front truck axle box 20, be provided with by driving the drive unit 8 that above-mentioned flexible supporting mechanism 6 changes the altitude datum L0 of compression spring 60.

For example as shown in Figure 7, can use oil gear as this drive unit 8.

In this structure, front truck axle box 20 is made up of vehicle body frame 10 sides fixing upper box body 20A and the fixing lower part box 20B of front-wheel 2 sides, and change relative upper-lower position by lower part box 20B corresponding to upper box body 20A and stretch, front axle 25 relatively moves along the vertical direction with respect to upper box body 20A, changes the height and position of front-wheel 2 along the vertical direction.

In this structure, the fexible bias pressure of pushing king pin 23 is installed between the spring receiving element 23c and piston 81 that is fixed on this king pin upper end with the first compression spring 60 downwards, and piston 81 is free to slide to be contained in the ground in the cylindrical chamber 80 integrally formed in the upper box body 20A of king pin 23 top positions.

In above-mentioned cylindrical chamber 80, provide the pressure oil of authorized pressure from oil pressure source not shown in the figures, piston 81 is arranged on is fit on the height and position.Thereby, utilize the operation of the pressure-regulating valve that does not show etc., freely change the setting oil pressure that is supplied to the pressure oil in the cylindrical chamber 80, set oil pressure by such change, and change the height and position of piston 81, owing to can change altitude datum based on flexible supporting structure 6, for example, corresponding to the superficial field of field, the deep field of field, can change the altitude datum of flexible supporting structure 6, walk.

In addition, the symbol 20Ac among the figure is at the inner integrally formed limiter of upper box body 20A, and it contacts the maximum slippage that limits according to the front axle 25 of flexible supporting mechanism 6 by the stop component 23c with king pin 23 upper ends.

(2) as shown in Figure 8, also can use the drive unit 8 of electric cylinder as the flexible supporting mechanism 6 that drives front truck axle box 20.

In this structure, use front truck axle box 20 when constituting drive unit 8 in the same manner with above-mentioned use oil gear, use electric cylinder to replace oil hydraulic cylinder.

Specifically, owing to utilize the electromotor 83 that is arranged on upper box body 20A upper end, by be rotated the spiral shell axle 84 of driving along both forward and reverse directions, carry out the upper-lower position adjustment of piston-like parts 82, central portion at piston-like parts 82 forms the threaded portion of meshing with spiral shell axle 84, in upper box body 20A, form prominent bar as the guide part 85 of preventing piston-like parts 82 to rotate, utilize the driving force of electromotor 83, by spiral shell axle 84, adjust the upper-lower position of piston-like parts 82, thereby change the altitude datum of flexible supporting mechanism 6.

(3) drive unit 8 of the swing supporting mechanism 7 that drives back axle case 30 also can be set

As shown in Figure 9, with respect to the 10A of vertical wall portion that is set at vehicle body frame 10 rear portions, around the 77 periphery swings of horizontal fulcrum top bearing object 71 is installed freely, will be arranged on end with the distolateral set side opposition side of axial region 71A of the trip of top bearing object 71 with oil hydraulic cylinder 86 as the adjusting of drive unit 8.Utilize described adjusting stretching with oil hydraulic cylinder 86, by making 71 swings of top bearing object around above-mentioned horizontal fulcrum 77 revolutions, change is with respect to the established angle of the 10A of vertical wall portion, change is born the position with respect to the upper end side of the second compression spring 70, by turning round around above-mentioned axis of pitch X, change the upper-lower position of back axle 36, can change the reference position of swing supporting mechanism 7.

Self-evident, also can adopt electric cylinder as drive unit 8.

(4) concrete structure of the swing supporting mechanism 7 that supports back axle case 30 as freely swinging, local is not limited to shown in Figure 5ly by the core 73 between trip end that is crossed on top bearing object 71 and the bottom bearing object 72 and be embedded in the structure that the compression of second on the core 73 spring 70 is formed outward, for example can adopt structure shown in Figure 9.

In this structure, forming hook portion 70a as the 2nd two ends of compressing the disc spring of spring 70, described hook portion 70a is hung on the axial region 71A of the trip end that is set at top bearing object 71 respectively and bottom bearing object 72 and the 72A, and the tubular conduit 78 of containment disc spring distortion is set in the outside of described disc spring.In tubular conduit 78, form the long notch portion 78a of the above-below direction that moves up and down that does not hinder the axial region 71A that carries out the 2nd compression spring 70 expanding-contracting actions.

(the 2nd example)

In the 2nd example, in the swing supporting mechanism of back axle case, the back axle case swing up and down fulcrum a, be positioned at from the point of the front end of the outward extending supporting arm in back axle case the place ahead different with the structure of first example.Hereinafter this is specifically described, uses the same reference numerals to represent, just be not introduced with the first example components identical.

In meeting the ride-type rice transplanter of this example, utilize the front wheel suspension structure meet flexible supporting mechanism 6 and meet the suspension structure for rear wheel of swing supporting mechanism 7, front-wheel 2 and trailing wheel 3 respectively by displacement up and down suspension.

(based on the front wheel suspension structure of flexible supporting mechanism 6)

In front wheel suspension structure shown in Figure 13, as shown in the figure, front-wheel 2 is installed on the front truck axle box 110, and front truck axle box 110 is made of upper box body 110a that is fixed on the body side and the lower part box 110b that is fixed on front wheel side.Mainly constitute the flexible supporting mechanism 6 of this example by front truck axle box 110 and bearing spring hereinafter described 137.

Can and can be contained in longitudinal drive shaft 134 and 2 groups of helical gear 135a, 135b in the upper box body 110a in the utilization around longitudinal axis P revolution along chimeric being installed on each upper box body 110a of lower part box 110b of longitudinal axis P direction slip displacement; 136a, 136b make from interior front axle 133 interlocks that are contained in the extended differential shaft 132 of differential attachment of the outer left of figure in the gear box 13 and are installed in the lower part box 110b to link to each other, thus the front-wheel 2 that driving links to each other with front axle 133.In addition, longitudinal drive shaft 134 belongs to lower part box 110b side, utilizes slip on the chimeric position of spline of helical gear 135b and longitudinal drive shaft 134 to absorb the displacement up and down of the longitudinal drive shaft 134 of the displacement up and down that is accompanied by lower part box 110b.In addition, above-mentioned longitudinal axis P tilts, and just has castor (with reference to Figure 10).

Between upper box body 110a and lower part box 110b, bearing spring (example of first spring) that the compression spring constitutes 137 by intercalation on above-mentioned longitudinal drive shaft 134, between power transmission shaft 134 and upper box body 110a and lower part box 110b.Thereby the body load that acts on the left and right sides front-wheel 1 is flexibly supported by bearing spring 137 separately respectively.

Bearing spring 137 is configured in telescopic spring stroke gamut with always being in compressive state.Utilize this structure, the elastic force of bearing spring 137 can correspondingly in telescopic spring stroke gamut be played a role well.

Figure 13 shows, bearing spring 137 is compressed maximum upward from place, the lower end altitude datum L0 (altitude datum that is equivalent to each front-wheel) of bearing spring 137 and allows that stroke only is S1 under the common user mode of body, just move to the state of maximum rising upper limit level face Lt (state of the following end in contact containment rising of the upper end of lower part box 110b and upper box body 110a).On the contrary, maximum allows that stroke S2 means that said reference height L0 and the maximum decline threshold level of bearing spring 137 face Lb are (under this state downwards downwards, the stop component 134a of the upper end side of longitudinal drive shaft 134 contact helical gear 135b is prevented the state of decline) between distance.Bearing spring 137 is configured in telescopic spring stroke gamut with always being in compressive state.

As mentioned above, L0 watches from altitude datum, because the ratio upper side of allowing travel settings of lower side allowed that stroke is big (just because S1＜S2=, moved upward to compare and can be contained more energetically that front-wheel 2 is absorbed in moving downward of causing by what front-wheel 2 rose and causes with containment, this is owing to allow stroke range containing can apply flexibly effectively when leaning forward the shallow generation of planting the floating seedling that causes that causes by body.

In addition, as shown in figure 17, knuckle arm 140 is connected on the lower part box 110b of the left and right sides, each knuckle arm 140 is connected to the pitman arm 141 of body central portion by steering tie rod 142 respectively, utilize the revolution operation of steering wheel 16, along gyratory directions, 2 each front-wheel steer about making.

(meeting the rear wheel suspension mechanism of swinging supporting mechanism 7)

In Figure 10～12 and Figure 14～19, shown this swing supporting mechanism 7.As shown in the figure, the back axle case 115 of carries left off hind wheel 3 is made up of with the deceleration box part 115b that links to each other with two ends, the central box part 115a left and right sides central box part 115a, be transfused to central box part 115a from the variable-speed dynamic of gearbox 13 outputs by first power transmission shaft 114, central box 115a and left and right sides deceleration box part 115b utilize pillar 117 that pipe makes downlink connection mutually, and whole box body is enhanced.Each supporting arm 151 forwards extends and is fixed on the described carriage 150 from the carriage 150 of the front, the left and right sides that is connected central box part 115a, and the support connecting rod 152 that becomes reverse U shape to form band plate material bending machining utilizes fulcrum pin 153 to be installed in the interior of left and right sides deceleration box 115b to extend on the side and upward.

The vehicle body frame 118 that cornue is made from gearbox 13 backward and be connected on the gearbox 13, fulcrum 154 left and right horizontal are connected on the connecting portion 118a of the longitudinal wall shape on the front portion of vehicle body frame 118 with connecting, and the front end boss 151a of the above-mentioned supporting arm 151 that extends forward from back axle case 115 is connected to the two ends of fulcrum 154 by rubber bush 155.The back axle case 115 that is supported like this is that fulcrum can swing up and down displacement with the axis a of the fulcrum 154 of forward profile away from trailing wheel 3 (outline of seeing from the side), and, utilize the elasticity adaptability of rubber bush 155, back axle case 115 integral body also can about fascinate.

In addition, in back axle case 115, in that fulcrum 156 is prominent forward not on the position of keeping right of central box part 115a, fulcrum pin 158 is darted at forward on the carriage 157 that is arranged at vehicle body frame 118 lower-left faces simultaneously, utilized rubber bush 160 to link to each other with fulcrum pin 158 with fulcrum 156 by two ends boss 159a, the 159b of the lateral rod of landscape configuration (lateral rod) 159, the oscillation crosswise of restriction back axle case 115 with lying across.In addition, the limiter 161 that rubber is made is set at about the rear portion of vehicle body frame 118, and the contacting of the top and limiter 161 by carriage 150 limited the hunting range of axle box 115.

In addition, at the rear portion of vehicle body frame 118, stand and establish the vertical framework 119 that pair of right and left connects the front end of the lifting linking member of being made up of quadric chain 41.Connect two ends that are fixed on the fulcrum 162 on this vertical framework 119 and the 163 connected whiles of slotted hole of passing through above-below direction from the top of the upwardly extending above-mentioned support connecting rod 152 in the left and right sides of back axle case 115 in left and right horizontal, to be installed in each by bearing spring (example of the 2nd spring) the 164 outer embeddings that the compression spring constitutes supports on the connecting rod 152, thereby the body load that acts on the left and right sides trailing wheel 3 is flexibly supported by left and right sides bearing spring 164.

At this moment, be supported on trailing wheel 3 on the back axle case 115 fulcrum a when swinging up and down displacement more forwards away from the profile of trailing wheel 3, and, owing to be positioned at height and position near trailing wheel axis height, the trailing wheel axis move up and down the arc track that track becomes the deep camber of near normal line.Thereby, even the big upward displacement of trailing wheel, particularly the displacement quantity of backward directions is very little along fore-and-aft direction, and the trailing wheel 3 after moving of rising is near plantation rice shoot device 4 sides, near the various mechanisms and the parts that are set at mounting rice shoot platform 45 front sides, but also do not contact these parts.

Figure 14 has shown the normal place in the flexible direction of the bearing spring 164 under the common user mode of body.From then on state maximum upward allow stroke S3 be among the figure the maximum rising upper limit level of the altitude datum L0 shown in bearing spring 164 lower ends (reference position that is equivalent to trailing wheel) and this lower end position face Lt (under this state, by the top contact limiter 161 of above-mentioned carriage 150, (fluctuating) confined state that fascinates of back axle case 115) distance between.Maximum downwards allows that stroke S4 is the distance between said reference height L0 and the bearing spring 164 maximum decline threshold level face Lb (at this state, the upper end side of the slotted hole 163 of above-below direction contacts with fulcrum 162, is in the state that descends of preventing).

Thereby, L0 watches from altitude datum, since with the ratio lower side of allowing travel settings of upper side allow stroke big (just because S3＞S4), compare by trailing wheel 3 moving downward of being absorbed in that recess causes with containment and can contain more energetically by trailing wheel 3 and rise and moving upward of causing to protuberance.So be provided with to apply flexibly effectively when being the generation of the floating seedling that causes in order to rise shallow the planting that cause by After-Body and allow stroke range in containment.

In addition, if change the different bearing spring 164 of coefficient of elasticity of elastic force and spring, the wobbling action scope of the back axle case 115 of just can sening as an envoy to and the different setting of swing performance.In addition, the coefficient of elasticity of the bearing spring 137 of the above-mentioned flexible supporting mechanism 6 of ratio that preferably is set of the coefficient of elasticity of bearing spring 164 is little.

The interior that in Figure 18 and 19, has shown back axle case 115.In the central box part 115a of back axle case 115, sending when the power shaft 170 of gearbox 13 power is assembled forward, horizontal power transmission shaft 171 by helical gear interlock is by willfully on power shaft 170, the power that transmits to this horizontal power transmission shaft 171 is sent to left and right sides trailing wheel 3 by left and right sides bifurcated by side clutch 172, gear reduction 173 and back axle 174.Laterally the axis of power transmission shaft 171 becomes the power Y-track b corresponding to left and right sides trailing wheel 3.When just the slave body side surface was seen, described power Y-track b was positioned at the inside of trailing wheel profile, and extend out (also with reference to Figure 11).

Shown in Figure 18～20, above-mentioned side clutch 172 is by the clutch gear 175 that is embedded in by trip on the horizontal power transmission shaft 171, be installed in clutch sleeve 176 on the horizontal power transmission shaft 171 by the outer embedding of spline, being inserted the inside bias voltage of clutch that is embedded on the horizontal power transmission shaft 171 forms with spring 177, spring 177 applies elastic force along the direction towards the casing center to clutch sleeve 176, be arranged on clutch gear 175 and extend the claw 175b on the projection section 175a and be arranged on claw 176a interlock on the clutch sleeve 176 by making, thereby enter the clutch state that transmits the power of horizontal power transmission shaft 171 to clutch gear 175.Make clutch sleeve antagonism spring 177, move laterally, remove the interlocking pattern of claw 175b, 176a, become and end from the clutch off-state of horizontal power transmission shaft 171 to the power transmission of clutch gear 175.

In addition, in the transmission downstream of this side clutch 172, the clutch operating according to continuing cut-off clutch can become deceleration-operation.Just little than clutch gear 175 diameters under drive gear 178 is installed on the horizontal power transmission shaft 171 with freely dallying, clutch gear 175 trip is embedded on the prolongation boss portion 178a of this gear 178, makes that to be formed on the claw 178b that prolongs on the boss portion 178a inner end relative with claw 176b on being formed on clutch sleeve 176 outer faces.Thereby, if clutch sleeve 176 is moved to foreign side from the elastic force that the clutch open position further resists spring 177, claw 176b and 178b interlock, the power that becomes horizontal power transmission shaft 171 is sent to the state of reduction gearing 178, and trailing wheel 3 more is being driven under the deceleration regime than clutch bonding state.

The medial end of above-mentioned clutch sleeve 176 is being assembled by butt joint on the relaying sleeve 180 of move operation according to the rotation that is installed in the operating axis on the central box 115a, be set at the clutch lever 181 on the main body outer end of operating axis 179 by rotating operation forwards, clutch sleeve 176 moves against the elastic force of spring 177, occurs " clutch bonding state ", " clutch off-state " shown in Figure 20 (b) and " decelerate state " shown in Figure 20 (c) shown in Figure 20 (a) successively.

In addition, above-mentioned clutch lever 181 is operated automatically with front-wheel steer action interlock.Just, as shown in figure 18, the rear tab 182 of the action bars 182 that rearward extends from about the pitman arm 141 is connected with left and right sides clutch lever 181 by slotted hole 183 and connecting pin 184.Thereby, in case pitman arm 141 from in-line position by swinging operation to more than the predetermined angular, front-wheel 2 is rotated more than the predetermined angular (for example 30 °) left or right turn, with respect to the clutch lever 181 that turns to inboard trailing wheel 3 rotating operation according to the action bars 182 of starts forwards and forwards.Turn to inboard side clutch 172 to be switched to " clutch off-state ", at the left and right sides front-wheel 2 that is diverted operation with under the three-wheel driving condition of the trailing wheel 3 outside turning to, the 1 little revolution rotation of walking fuselage, in case front-wheel 2 is by bigger steering operation, the approximate boundary that reaches, clutch lever 181 is bigger ground rotating operation forwards, causes above-mentioned " deceleration-operation state ".At the left and right sides of steering operation front-wheel 2, turn to the trailing wheel 3 in the outside and be decelerated under the four wheel drive state of the inboard trailing wheel 3 of turning to of driving the 1 little revolution rotation of walking fuselage.

(the change example of second embodiment)

The present invention also can implement according to following form.

(1) Fig. 1 does not show, can set up above-mentioned transverse bar 159 on position, back and the vehicle body frame 118 with lying across and implement the present invention leaning on of supporting arm 151.

(2) in second example, pair of right and left supporting arm 151 forwards extends from the back axle case 115 of carries left off hind wheel 3, can be that the center swings up and down with the place ahead fulcrum a, and, shown in the occasion of can left and right directions supporting with fascinating, the supporting arm 151 that rigidity is big forwards extends from back axle case 115, by rubber bush 155,151a is connected on the fulcrum 154 with its front end boss portion, can implement second example.

(3) can make elasticity support the bearing spring 164 of back axle case 115 to have big diameter, make it to act on the state of casing central portion, implement the present invention.

(4) as the unnecessary means that laterally move of restriction back axle case 115 and supporting arm 151, except utilizing transverse bar 159, can adopt the structure that laterally moves the control guiding parts that dock is set at positions such as bearing spring installation portions.

(5) in one of first, second example, for the front wheel suspension structure, the linear telescopic according to flexible supporting mechanism 6 can make each front-wheel move up and down.Replace the scheme of this pattern to be, adopt in two examples such mechanism of swing supporting mechanism 7, can utilize also that non-rectilinear is flexible to move up and down each front-wheel.

(the 3rd example)

Hereinafter the 3rd example is described, used the same reference numerals to represent, this just no longer has been introduced with former example components identical.In addition, in this example, the side clutch is transverse box body in the back axle case not, but is configured in the longitudinal deceleration chest portion.

Shown in Figure 22～24, the reduction box body 210B that rear wheel drive freely is supported on the horizontal back axle case 210A of portion of vehicle body frame 10 with back axle case 210 by front and back axis R periphery certain limit inherence and is connected its two ends, left and right sides respectively constitutes.In the horizontal back axle case 210A of portion, the horizontal power transmission shaft 241 that the power left and right sides runout of first power transmission shaft 14 that interior dress extends back since gearbox 13 in the future distributes makes the helical gear interlock on first power transmission shaft 14.In addition, support trailing wheel 3 back axle 242, the reduction gear arrangement 243 of horizontal power transmission shaft 241 and back axle 242 retarded motions is assembled among each reduction box body 210B.

And intermittently the friction-type side clutch 245 that transmits power to each trailing wheel 3 is installed between the two ends and each reduction gear arrangement 243 of horizontal power transmission shaft 241.Side clutch 245 comprises boss parts 246 and the slave end rotating cylinder 247 that links with reduction gear arrangement 243, boss parts 246 are entrenched on the horizontal power transmission shaft 241 by spline, and with horizontal power transmission shaft 241 unitary rotation in can move freely along axis direction, mutual on boss parts 246 and the slave end rotating cylinder 247 in conjunction with a plurality of friction plates 248 are installed, move the mutual crimping interlock (clutch in conjunction with) that rubs by boss element 246 to the horizontal foreign side of fuselage, move by boss element 246 side in the fuselage horizontal stroke simultaneously and removing friction interlock (cut-off clutch), make boss parts 246 to clutch in conjunction with clutch spring 249 quilts of side shifting outside embedding be installed on the horizontal power transmission shaft 241.

In addition, shown in Figure 23 and 24, stop fuselage and be installed between the boss parts 246 of right side reduction box body 210B and right side side clutch 245 with brake 250.By make the outer embedding of spline be installed on above-mentioned boss parts 246 peripheries friction plate 251 and by with reduction box body 210B in week combine friction plate 252 crimping of preventing rotation, 250 pairs of boss parts 246 of described brake and brake with the horizontal power transmission shaft 241 of boss parts 246 unitary rotation.Be embedded in cup-shaped functional unit 253 on the boss parts 246 by moving by trip, make friction plate 251,252 crimping each other to the horizontal foreign side of fuselage.

Stopping fuselage operating around the brake-operating spindle 254 that longitudinal axis P1 above the reduction box body 210B connects installation freely to rotate with brake 250 utilizations.When just in the main body that mobile shift fork 255 is installed in brake-operating spindle 254, charging on the part, these mobile shift fork 255 end faces with aforesaid operations parts 253 that be set up are relative, by brake-operating spindle 254 is rotated, utilize mobile shift fork 255, functional unit 253 is moved, can brake boss parts 246.

And, as shown in figure 24, be set on the outer protuberance of main body of above-mentioned brake-operating spindle 254 action bars 254a by connecting rod 257 be arranged on running portion in take right front pedal 56 interlocks in the underfooting of portion and link to each other, be accompanied by the operation of trampling of pedal 56, make connecting rod 257 displacement that forwards stretches, brake 250 is braked.Remove the described operation of trampling, just removed the braking action of brake 250.Utilize the fixing maintenance of check lock lever 58 (Fig. 2) to be trampled the pedal 56 of operation, can cause dead ship condition.In addition, omitted detailed structure, the left part that connects the fulcrum 56a of pedal 56 is connected to the operation system of static oil pressure endless gearing device (example of stepless speed change device) 12 by mechanism, in case pushes pedals 56 is returned the neutral position at the main shift lever 232 (Figure 21) that advances the territory or retreat territory operation with being compelled to.

The operating structure of above-mentioned side clutch 245 has following structure.Just, utilize the outstanding clutch operating sleeve 261 that is arranged on the end face of above-mentioned boss parts 246 of thrust ring 260 butt joints, when utilizing spline to be arranged on the horizontal power transmission shaft 241 by slotting embedding, the clutch operating axle 262 quilt perforations of freely rotating around longitudinal axis P2 be installed in reduction box body 210B above, be formed on relative configuration of end face of the eccentric cam 263 charged in the main body of this clutch operating axle 262 on the end and aforementioned clutch operating sleeve 261, utilize the rotating operation of clutch operating axle 262, make side clutch 245 connect opening operation.In addition, as shown in figure 22, the phase place of eccentric cam 263 is according to following state setting: rotate along the counter clockwise direction of seeing on the plane by the clutch operating axle 262 that makes left side side clutch 245, clutch is disconnected, by clockwise rotating, keep the clutch on-state, in addition, as shown in figure 22, rotate along the clockwise direction of seeing on the plane by the clutch operating axle 262 that makes right side side clutch 245, clutch is disconnected,, keep the clutch on-state by rotating counterclockwise.

And, only also being furnished with when front-wheel 2 is above from in-line position steering operation predetermined angular automatically, opening operation goes back to inboard side clutch 245, the automatic changeover A of the fuselage revolving force that causes because of the difference of left and right sides trailing wheel propulsion capability, hereinafter the concrete structure to automatic changeover A describes.

As shown in figure 24, the pitman arm 265 that swings at the rotary manipulation that utilizes steering wheel 16 and around longitudinal axis Z by steering tie rod 267 respectively with the joint arm 266 of front-wheel 2 be connected constitute linkage 268 in, be connected on the pitman arm 265 operation joint 265a with can link to each other by stretching bar 270 around the relay arm 269 that longitudinal axis core S is not swingingly put near the bottom fuselage fore-and-aft direction pars intermedia, the intermediate arm 271 and the relay arm 269 that center on longitudinal axis S cantilevered swing are provided with integratedly.By the bar 272 as linkage part, two ends, intermediate arm 271 left and right sides are connected with the action bars 262a that is connected with on the body protuberance of clutch operating axle 262.

In addition, by slotted hole 273 on the rear portion joint 272a that is formed on bar 272 and the coupling pin 274 of action bars 262a, bar 272 and action bars 262a keep being connected compatiblely, in case bar 272 is forwards by big stretched operation, be urged at the rear end of slotted hole 273 coupling pin 274, action bars 262a disconnects the direction rotation along clutch, even rearward press described bar 272, slotted hole 273 only rearward moves with respect to coupling pin 274, and action bars 262a can not rotating operation.

If selection said structure, in common plantation operation, the steering angle of front-wheel 2 is littler than predetermined angular, swing intermediate arm 271, the bar 272 of one side is drawn forward stretches operation, and slotted hole 273 and coupling pin 274 only relatively move, and action bars 262a is rotating operation not, keep right and left side clutch 245 and be co-located on on-state, trailing wheel 3 constant speed in the left and right sides are driven.

On furrow, in order to change the fuselage direction, in case make front-wheel 2 when left or the wide-angle more than the right-hand rotation predetermined angular, the bar 272 of one side is drawn forward with can exceeding slotted hole 273 allowances, be equivalent to go back to the action bars 262a of inboard side clutch 245 along clutch disconnection direction rotary manipulation, thereby, utilize three wheel drive of left and right sides front-wheel 2 and the off hind wheel 3 that goes back to the outside, the fuselage rotation, the trailing wheel 3 that goes back to the inboard that side clutch 245 disconnects is accompanied by the mobile ground connection of rotation of fuselage and complies with, can dally, go back to inboard trailing wheel 3 and can locally destroy the field, can carry out the fuselage rotation.

Said structure identical with function (for example opening flat 2002-264835 communique) with reference to the spy of Japan with existing automatic changeover, but in the present invention, add following structure.

Shown in Figure 24 and 25, by anterior joint 272b, disconnect the front end of each bar 272 that is connected the action bars 262a of the two ends of the described intermediate arm 271 that is connected and side clutch 245 with reciprocating motion with the single action type oil hydraulic cylinder 281 of oil cylinder as the side clutch.

In a single day oil hydraulic cylinder 281 is provided pressure oil and just carries out contractile motion, in case the inner shock mount 283 of oil extraction extends action.Oil hydraulic circuit as shown in figure 26 utilizes electromagnetic type control valve 284 to carry out control operation.In addition, in Figure 26, the torque sensor that on behalf of hydraulic steering, symbol 285 use, the Electromagnetic Control valve assembly that the above-mentioned lifting of symbol 286 representative management is moved with oil hydraulic cylinder 5.

With reference to Figure 24～26, usually, above-mentioned control valve 284 is in non-excited state, and two oil hydraulic cylinders 281 receive the pressure oil of supplying with, and become state under reach.At this moment, the connection length that comprises the bar 272 of oil hydraulic cylinder 281 is in standard state.And turning to from in-line position more than the predetermined angular (for example 30 °) as if front-wheel 2 under this standard state, as mentioned above, the side clutch 245 that goes back to inboard trailing wheel 3 carries out opening operation automatically.

And above-mentioned control valve 284 utilizes control device 287 to carry out following control action.Just, front-wheel 2 detects from the steering evaluator 288 that turns to the θ angle to be made up of potentiometer or rotary encoder etc. of in-line position, and is input to control device 287, finds that front-wheel 2 turns to above predetermined angular θ from in-line position in case detect ₀More than, shown in Figure 25 (b), energising is controlled in the t at the appointed time off and in control valve 284 period T ground, switch between the energising excitation at control valve 284, two oil hydraulic cylinders 281 carry out oil extraction, inner shock mount 283, extend action, the connection length of two bars 272 is elongated.

In this case, though with the interlock that turns to more than front-wheel 2 predetermined angulars, a bar is drawn forward and stretches, go back to inboard side clutch 245 and have off-state, since bar 272 only above-mentioned control valve 284 be energized the connection length of excitation rod 272 elongated during displacement rearward, the going back to inboard side clutch 245 and can recover on-states of disconnection.And stopping the energising excitation of control valve 284, oil hydraulic cylinder 281 carries out contractive action, in case the connection length of bar 272 is shortened standard state, goes back to inboard side clutch 245 and becomes off-state at this.Be accompanied by the intermitten of control valve 284, go back to inboard side clutch 245 according to the rules period T only at the appointed time a (=T-t) be disconnected operation off and on.

In addition, utilize the intermitten of control valve 284, the connection length of the bar 272 of the side clutch 245 on the trailing wheel 3 outside manipulation goes back to changes equally, owing to utilize the compatibility of slotted hole 273 to absorb its variation, be not sent to action bars 262a, the side clutch 245 that goes back to the outside is kept on-state.

Consider various control valve 284 is carried out the intermittently power-on excitation and makes side clutch 245 indicatrix of off-on off and on of the trailing wheel 3 that goes back to the outside, be explained hereinafter.

(first example): shown in Figure 27 (a), automatic changeover A is started, at the steering angle θ of front-wheel 2 from afore mentioned rules angle θ ₀To steering locking angle degree θ _mGamut in, at some cycles T, with the regulation clutch a turn-off time ₁Give control valve 284.

(second example): shown in Figure 27 (b), automatic changeover A is started, at the steering angle θ of front-wheel 2 from afore mentioned rules angle θ ₀To steering locking angle degree θ _mGamut in, at each some cycles T, give clutch a turn-off time of regulation ₁The time, return in the craspedodrome stroke at front-wheel 2, than predetermined angular θ ₀Big regulation angle θ ₁Stop excitation.Early connect and go back to inboard side clutch 245.

(the 3rd example): shown in Figure 27 (c), automatic changeover A is started, at the steering angle θ of front-wheel 2 from afore mentioned rules angle θ ₀Extremely than its first bigger predetermined angular θ ₁Opereating specification in, at each some cycles T, give clutch a turn-off time of regulation ₁, from the first predetermined angular θ ₁Extremely than its second bigger predetermined angular θ ₂Opereating specification in, at each some cycles T, give than above-mentioned clutch a turn-off time ₁Big regulation clutch a turn-off time ₂, and from the second predetermined angular θ ₂To steering locking angle degree θ _mGamut in, at each some cycles T, give than above-mentioned clutch a turn-off time ₂Big regulation clutch a turn-off time ₃

Front-wheel steer angle just is more big, and average clutch stage turn-off time is long more, has improved little verticity.

(the 4th example): shown in Figure 27 (d), automatic changeover A is started, at the steering angle θ of front-wheel 2 from afore mentioned rules angle θ ₀To steering locking angle degree θ _mGamut in, at each some cycles T, clutch a turn-off time that is endowed increases continuously and linearly.Thereby the front-wheel steer angle is big more, and average clutch is long more turn-off time, and little verticity progressively improves.

(the 5th example): shown in Figure 27 (e), automatic changeover A is started, at the steering angle θ of front-wheel 2 from afore mentioned rules angle θ ₀Extremely than steering locking angle degree θ _mLittle angle θ ₂Scope in, at each some cycles T, clutch a turn-off time that gives is increased continuously and linearly; From above-mentioned angle θ ₂To steering locking angle degree θ _mOpereating specification in, every some cycles T, give clutch a turn-off time ₁At front-wheel 2 from steering locking angle degree θ _mReturn in the craspedodrome stroke, from above-mentioned steering locking angle degree θ _m, at each some cycles T, clutch a turn-off time that gives is diminished continuously and linearly, than predetermined angular θ ₀Big predetermined angular θ ₁Stop excitation, early connect and rotate back to inboard side clutch 245.

(the 6th example): shown in Figure 27 (f), automatic changeover A is started, at the steering angle θ of front-wheel 2 from afore mentioned rules angle θ ₀To steering locking angle degree θ _mGamut in, at each some cycles T, clutch a turn-off time that gives is increased continuously and linearly, at steering locking angle degree θ _mThe time clutch turn-off time be a ₁Even so, also be that the front-wheel steer angle is big more, average clutch a turn-off time is long more, and little verticity sharply uprises.

In addition, the oil hydraulic cylinder 281 former states elongation that occurs owing to the fault of electric control system but can not shrink the time, the link position of adjusting lever 272 anterior joint 272b and oil hydraulic cylinder, is standard state to comprise oil hydraulic cylinder in the connection length of interior bar 272, make the automatic changeover A can start, in case the front-wheel steer angle becomes predetermined angular θ ₀More than, just opening operation rotates back to the side clutch 245 (with reference to Figure 24) of inboard trailing wheel 3 continuously.

(the 3rd example Change Example)

The present invention also can implement by following form.

(1) in above-mentioned example, a pair of oil hydraulic cylinder 281 on the bar 272 that two ends and the right and left side clutch 245 that is assembled in intermediate arm 271 is connected is connected on the single control valve 284, make the 281 equidirectional starts simultaneously of two oil hydraulic cylinders, but also can make the intermittently start between neutral position and another switching position of three position suitching type control valves, only make side clutch 245 disconnect the oil hydraulic cylinder 281 intermittently starts of side.

(2) in above-mentioned example, to be assembled in a pair of bar interlock that is connected with intermediate arm 271 and right and left side clutch 245 as the oil hydraulic cylinder 281 of the side clutch reciprocating movement oil cylinder that off-on is used at intermittence respectively fastens, also can be with can be in neutrality, the reciprocating movement oil cylinders such as oil hydraulic cylinder that shrink and extend 3 positions switchings are assembled in the bar interlock that is connected with pitman arm 265 and relay arm 269 and fasten, when described stretching bar 270 anticlockwises of bulldozing operation rearward, make reciprocating movement oil cylinder repeat neutral and the contraction start, connection disconnects control left side clutch 245 off and on; When described stretching bar 270 right rotations of stretched operation forwards, make reciprocating movement oil cylinder repeat neutral and the elongation start, connect off and on and disconnect control right side clutch 245.

(3) in above-mentioned example, as mentioned above, make clutch a turn-off time stage ground or variation continuously at each some cycles T, make the front-wheel steer angle big more, average clutch is long more turn-off time, progressively to improve little verticity, clutch a turn-off time is certain each time but also can make, when front-wheel steer angle θ is big more, make interim ground of period T or minimizing continuously simultaneously, make average clutch within a certain period of time elongated turn-off time.

(4) in above-mentioned example, exemplified and made left and right sides trailing wheel 3 have speed difference, performance makes to go back to the intermittently form of opening operation of inboard side clutch 245 during verticity, but also can be by carrying out side clutch opening operation continuously the form of brake side brake implement.

(5) in above-mentioned example, will handle front-wheel 2 and turn to above predetermined angular θ ₀, the automatic changeover A that the side clutch 245 that goes back to inboard trailing wheel 3 is carried out the automatic disconnection operation constitutes mechanical type, utilizes this automatic changeover A, makes the side clutch 245 that is disconnected connect start off and on.But also can make right and left side clutch respectively independent, only constitute and to carry out on-off operation, and surpass predetermined angular θ by transmission device ₀Front-wheel steer interlock, only make a side transmission device action, with the described side clutch 245 that goes back to the trailing wheel 3 of inboard of desirable characteristic on-off control.

(6) in the above-described embodiments, the linkage part that is connected as the action bars 262a with intermediate arm 271 and side clutch 245 has utilized bar 272, also can utilize iron wire as linkage part.

(7) connect the reciprocating movement oil cylinder of disconnection off and on as the side clutch that makes start according to automatic changeover A be disconnected operation, except utilizing the oil hydraulic cylinder of being controlled by start according to above-mentioned control valve 284 281, also can utilize according to control device 287 by electric transmission devices such as directly actuated electric cylinder and os.

(other association)

Be example with the ride-type rice transplanter above, various examples are described, the present invention is also applicable to other ride-type paddy field machines such as sower, tree-removers.

Claims (11)

1 one kinds of ride-type paddy field machines comprise being bearing in front truck axle box (20; 110) front-wheel on (2) and be bearing in back axle case (30; 115) trailing wheel on (3) is characterized in that, also comprises: distinguish above-mentioned front-wheel of independent suspension (2) and the flexible supporting mechanism (6) that can move up and down, make aforementioned trailing wheel (3) with the transverse axis center (X along the fuselage left and right directions; But a) the swing supporting mechanism (7) of revolution above-below direction swing.

2 ride-type paddy field machines according to claim 1 is characterized in that: utilize above-mentioned swing supporting mechanism (7), respectively each trailing wheel of suspension (3) independently.

3 ride-type paddy field machines according to claim 1 is characterized in that: above-mentioned back axle case (115) is as single casing setting, with each trailing wheel (3) mounting support on this single casing.

4 as ride-type paddy field machine as described in the claim 3, it is characterized in that: extend by the front end of the supporting arm (151) that forwards stretches out from above-mentioned back axle case (115) at the aforementioned transverse axis center (a) of above-mentioned swing supporting mechanism (7), with this transverse axis center (a) as fulcrum, above-mentioned back axle case (115) but easy on and off swing and to the left and right direction connect obliquely and be bearing on the walking fuselage (1).

5 as ride-type paddy field machine as described in the claim 4, it is characterized in that: in above-mentioned flexible supporting mechanism (6), be provided with and distinguish independent and first spring (137) of displacement ground each front-wheel of elastic bearing (2) up and down, in above-mentioned swing supporting mechanism (7), be provided with second spring (164) of the above-mentioned back axle case of elastic bearing (115).

6 as ride-type paddy field machine as described in claim 4 or 5, it is characterized in that: the restraint device that laterally moves that is provided with the above-mentioned back axle case of restriction (115).

7 as ride-type paddy field machine as described in the claim 6, it is characterized in that: in above-mentioned swing supporting mechanism (7), the above-mentioned supporting arm of pair of right and left (151) is set, and, be provided with the bearing spring (164) of the above-mentioned back axle case of elastic bearing (115), above-mentioned restraint device comprises the transverse bar (159) that is erected between above-mentioned back axle case (115) or supporting arm (151) and the vehicle body frame (118).

8 ride-type paddy field machines according to claim 1, it is characterized in that: under the effect of above-mentioned flexible supporting mechanism (6), allow stroke (S2) than allowing that to shrinkage direction stroke (S1) is big to prolonging direction from said reference height (L0) from the altitude datum (L0) of each front-wheel (2).

9 ride-type paddy field machines according to claim 1, it is characterized in that: under the effect of above-mentioned swing supporting mechanism (7), from the reference position (L0) of above-mentioned trailing wheel (3) to uplifted side allow stroke (S3) than from said reference position (L0) to the lower side allow that stroke (S4) is big.

10 ride-type paddy field machines according to claim 1 is characterized in that: above-mentioned flexible supporting mechanism (6) comprises first spring (60 that is made of the compression spring; 137), this first spring (60; 137) in the gamut of whole telescopic spring stroke, always be in compressive state.

11 as ride-type paddy field machine as described in the claim 10, it is characterized in that: above-mentioned swing supporting mechanism (7) comprises second spring (70) that is made of the compression spring, and the coefficient of elasticity of this second spring (70) is littler than the coefficient of elasticity of above-mentioned first spring (60).

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