KR100658009B1 - Riding-type Paddy Field Working Machine - Google Patents

Abstract

A passenger type non-non-working machine having a front wheel (2) supported on the front axle case (20) and a rear wheel (3) supported on the rear axle case (30), wherein each of the front wheels (2) is independently suspended. An elastic support mechanism (6) capable of vertical movement and a swing support mechanism (7) capable of swinging the rear wheel (3) in the vertical direction around a horizontal axis center (X) along the machine body left and right directions Brother Munnon is a working machine.

Axle case, front wheel, rear wheel, swing support mechanism, telescopic support mechanism

Description

Riding-type Paddy Field Working Machine}

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is an overall side view of a first embodiment of the present invention, and showing a riding type transfer machine as an example of a riding type munon work machine.

FIG. 2 is an overall plan view of the electric machine of FIG. 1; FIG.

Fig. 3 is a front view of the front wheel suspension structure in the transfection machine of Fig. 1;

Fig. 4 is a plan view showing an electric system having a rear wheel suspension structure in the transfer machine of Fig. 1;

Fig. 5 is a side view of the rear wheel suspension structure in the transfection machine of Fig. 1;

Figure 6 is a plan view of the rear wheel suspension structure of Figure 5;

FIG. 7 is a side view showing another modification of the front wheel suspension structure in the transfer machine of FIG. 1; FIG.

FIG. 8 is a side view showing still another modification of the front wheel suspension structure in the transfer machine of FIG. 1; FIG.

Fig. 9 is a side view showing a modification of the rear wheel suspension structure in the transfer machine of Fig. 1;

Fig. 10 is an overall side view of a second embodiment of the present invention, showing a riding type electric machine as an example of the riding type munon work machine according to the present embodiment.

Fig. 11 is a side view showing the suspension structures of the front wheels and the rear wheels in the transfer machine of Fig. 10;

12 is a plan view showing the suspension structure of FIG.

FIG. 13 is a front view showing the front wheel suspension structure of FIG. 12; FIG.

Fig. 14 is a side view showing the rear wheel suspension structure in the transfection machine of Fig. 10;

Fig. 15 is a plan view showing the rear wheel suspension structure of Fig. 14;

FIG. 16 is a front view showing the rear wheel suspension structure of FIG. 15; FIG.

Fig. 17 is an overall plan view showing a machine body steering structure in the transfection machine of Fig. 10;

Fig. 18 is an exploded cross-sectional view showing the internal structure of the rear wheel drive rear axle case in the transfer machine of Fig. 10;

Fig. 19 is a sectional view showing a main part of a rear axle case for rear wheel driving in the transfer machine of Fig. 10;

Fig. 20 is a sectional view showing the operation of the side clutch in the transfer machine of Fig. 10;

Fig. 21 is an overall side view of the third embodiment of the present invention, and showing a riding type electric machine as an example of the riding type munon work machine according to the present embodiment.

Fig. 22 is a longitudinal rear view of the left side clutch in the transfection machine of Fig. 21;

FIG. 23 is a longitudinal rear view of the right side clutch and brake of the transfer machine shown in FIG. 21;

Fig. 24 is a schematic plan view of the automatic steering mechanism in the transfer machine of Fig. 21;

FIG. 25 is a plan view showing a main part of the automatic steering mechanism of FIG. 24; FIG.

FIG. 26 is a hydraulic circuit diagram of the transfer machine of FIG. 21;

Fig. 27 is a diagram showing the side clutch operating characteristics in the transfer machine of Fig. 21;

<Explanation of symbols for main parts of the drawings>

1: driving machine body

2: front wheel

3: rear wheel

6: elastic support mechanism

7: rocking support mechanism

20, 110: front axle case

30, 115: rear axle case

60, 137: first spring

70, 164: second spring

118 body frame

151: support arm

159: side load

L0: Reference level (reference position)

S1: permissible stroke in the contracting direction of the elastic support mechanism

S2: permissible stroke in the extension direction of the elastic support mechanism

S3: Permissible stroke to the upper side of the swing support mechanism

S4: Permissible stroke to the downward side of the swing support mechanism

X, a: horizontal axis center (swing axis center of the swing support mechanism)

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a riding type munon work machine such as a riding type transfer machine having a front wheel supported by the front axle case and a rear wheel supported by the rear axle case. More specifically, the present invention relates to a riding type munon work machine characterized by its wheel suspension structure.

As a gear suspension structure of a riding type electric machine, which is a representative example of a riding type Munon work machine, a rear rear axle which supports the left and right front wheels in a mission case fixed to the front of the machine body and rollably supports the rear of the machine body. Supporting the left and right rear wheels to the case (for example, see Japanese Patent Laid-Open No. 2003-102215), while supporting the left and right front wheels to the mission case fixed to the front of the machine body, The rear wheels are journaled to the rear end portions of the left and right swing cases that extend toward each other so that the left and right rear wheels can be independently displaced (see, for example, Japanese Patent Laid-Open No. 2003-81140). Known.

In the riding type electric machine, when the high-speed traveling in the field site, the machine main body shaking and vibration caused by the irregularities in the field become severe, and the riding comfort is aggravated, and the position and posture of the parent transplant apparatus connected to the rear of the machine main body It becomes easy to change significantly, and even if it carries out automatic lifting control of a mother implantation apparatus, it cannot fully respond, and there exists a possibility that the implantation depth precision may fall. Therefore, there is a limit to speeding up the transplant running speed in actual work, and it becomes difficult to perform efficient transplant work by fully utilizing the capacity of the electric machine.

In particular, the change in posture of the main body of the machine caused by the rear wheels located immediately before the parent implant device through the oblique irregularities is large, and the influence on the position and posture change of the parent implant device is large, and the suspension structure of the rear wheel is There is a need to improve.

Here, according to what is disclosed in Japanese Patent Laid-Open No. 2003-102215, the rear-side transmission case in which the left and right front wheels are attached to and supported by a mission case fixed to the front of the machine body, and rollably supported to the rear of the machine body ( Since it corresponds to the rear axle case of this invention, it is the specification which supported the left and right rear wheels to the rear axle case hereafter. In this specification, the suspension function due to the rolling of the rear axle case is exhibited with respect to the difference between the left and right heights of the heel on which the rear wheels travel, and the main body of the machine is suppressed from greatly inclining from side to side. There is no suspension function when reaching the concave or convex, so that the rear of the machine main body is largely settled or lifted. In addition, the front wheel to which the fixed mission case is directly mounted does not have a suspension function, of course, so that the front wheel follows the unevenness of the head, causing a change in posture in the traveling machine body.                         

On the other hand, according to what is disclosed in Japanese Patent Laid-Open No. 2003-81140, the left and right swing cases protruding rearward from the mission case while supporting the left and right front wheels are mounted and supported on the mission case fixed to the machine body front part. The rear wheels are journaled to the rear end of the rear wheel, and the rear wheels on the left and right are independently elastically supported so that they can be vertically displaced. In this specification, the difference between the left and right heights of the heel of which the rear wheels travel is effectively absorbed by the independent suspension function of the left and right swing cases, and even when the left and right rear wheels simultaneously reach the recesses or convexities of the heel. The function can be sufficiently exerted to suppress large back and forth fluctuations (pitching) of the traveling machine body.However, since the front wheels are not equipped with a suspension function, the machine body posture changes when the front wheels pass through irregularities. There is room for improvement.

The present invention has been made in view of such a point, and an object of the present invention is to provide a suspension function on the front wheels and the rear wheels so as to smoothly drive a high speed in a field.

In order to achieve the above object, the riding type munon work machine according to the present invention has a front wheel supported on the front axle case and a rear wheel supported on the rear axle case, each of the front wheels, each independent suspension And an elastic support mechanism capable of moving up and down and a swing support mechanism capable of oscillating the rear wheel in a vertical direction around a horizontal axis center along the machine body left and right directions,
The rear axle case is provided as a single case member, and each rear wheel is mounted and supported on the single case member,
The center of the transverse axis of the swing support mechanism extends through the front end of the support arm which protrudes forward from the rear axle case,
The rear axle case is connected to and supported by the traveling machine main body so as to be able to swing up and down using the center of the horizontal axis as a supporting point.

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According to the above configuration, for example, when the rear wheel consists of a pair of left and right rear wheels, the rear axle case moves up and down in parallel when the left and right rear wheels simultaneously reach the raised portion or the concave portion in the light plate. The rear wheels simultaneously move up and down in the same direction, and large back and forth tilting (pitching) of the traveling machine main body is suppressed.

In addition, each front wheel follows the unevenness of the surface by the expansion and contraction action of the elastic support mechanism, thereby suppressing the change in the posture of the front part of the machine main body.
In one suitable embodiment, the said elastic support mechanism is provided with the 1st spring which elastically supports each front wheel so that up-and-down displacement is independent, and the said swing support mechanism is the 2nd spring which elastically supports the said rear axle case. Is installed.

In one suitable embodiment, a restricting means for limiting lateral movement of the rear axle case is provided. According to the above configuration, for example, when the rear wheel is made up of a pair of left and right rear wheels, an effect that can effectively exhibit the desired suspension function on the left and right rear wheels by limiting unnecessary lateral movement of the transmission case and the support arm Exert.

In this case, the left and right pairs of support arms are provided on the swing support mechanism, and a suspension spring for elastically supporting the rear axle case is provided, and the restricting means is provided between the rear axle case or the support arm and the body frame. It is also suitable to have a hypothetical side rod. In this configuration, the transmission case can be stably supported by the left and right support arms arranged at intervals in addition to the above-described effects, and the machine body loads applied to the left and right rear wheels are arranged at right and left intervals. Suspension springs ensure accurate and stable support.

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Other features of the riding type munon work machine according to the present invention, and operational effects and advantages exerted from such a configuration will become apparent by reading the following description with reference to the accompanying drawings.

EMBODIMENT OF THE INVENTION Hereinafter, the riding type munon work machine which concerns on this invention is demonstrated based on the riding type electric machine as an example of a riding type munon work machine, referring drawings.

[First Embodiment]

[Overall constitution of passenger electric machine]

Fig. 1 shows the whole side of a passenger transponder, and Fig. 2 shows the entire plane thereof.

This riding machine is designed to swing up and down by the operation of the hydraulic cylinder 40 at the rear portion of the riding type traveling machine main body 1 having a left and right pair of front wheels 2 and a left and right pair of rear wheels 3. 8 pairs constructed of mid-mount fertilization specifications by connecting an 8-row planting parent implant device 4 via an elevating link 41 formed of a 4-link link mechanism and equipped with an 8-roll fertilizer application device 5. A planting riding machine is constructed.

As shown in Figs. 1 and 2, the traveling machine main body 1 is a belt type transmission device 11 and a hydrostatic type mounted on the vehicle body frame 10 for power from the engine E mounted at the front thereof. The transmission is transmitted to a gear transmission (not shown) built into the mission case 13 via an HST or hydrostatic transmission 12, and for driving from the gear transmission. It is comprised so that a power may be transmitted to the left and right front wheels 2 via the front wheel drive device 21 built in the left and right front axle cases 20. Regarding the left and right rear wheels 3, the rear wheel drive device 31 incorporated in the first transmission shaft 14 and the rear axle case 30 in the front-rear direction to which the output from the mission case 13 is transmitted is It consists of a four-wheel drive type that is transmitted to the left and right rear wheels (3).

The traveling machine main body 1 includes a control part cover 15 incorporating the engine E, a steering wheel 16 provided above the steering wheel 16 for steering the left and right front wheels 2, and a passenger part floor ( 17) and a boarding driver provided with a driver's seat 18 and the like.

As shown in Fig. 1 and Fig. 2, the parent implantation apparatus (an example of the working apparatus) 4 includes five stationary floats 42 for stopping the mother transplantation site of the field surface H in advance with the running of the machine main body. ). In addition, the work force from the mission case 13 is transmitted to the feed case 44 via the 2nd transmission shaft 43, and the mother mounting table which loads 8 trillion bundles with the distribution power from the feed case 44 is carried out. 45 is reciprocally driven by a predetermined stroke in the left-right direction. At the same time, eight rotary implant mechanisms 46 arranged at predetermined intervals in the left and right directions take out a predetermined amount of hair from the lower end of the mother mounting table 45 and carry out a transplanting operation for transplanting them into the field. It is configured to be able to plant. In addition, the code | symbol 9 of a machine main body front part is a spare mother mounting stand.

The fertilizing device 5 has a groove digging mechanism 47 equipped in the stationary float 42 to form a fertilizing groove so as to correspond to each transplantation tank as the machine main body travels, while the eight feeding mechanisms 50 perform the mission. The fertilizer in the fertilizer hopper 51 is dispensed by a predetermined amount by the working power from the case 13, and the fertilizer dispensed from each feeding mechanism 50 by the operation of the electric fan 52 is handled through the guide hose 53. It is comprised so that a fertilizer may be buried in the horizontal part of the transplantation simulation in a field site by sending it toward the groove | channel digging mechanism 47 to make.

The suspension structure which supports the front and rear wheels in this riding machine is comprised as follows.

[Front wheel suspension structure by telescopic support mechanism 6]

The expansion and contraction support mechanism 6 includes a first compression spring (an example of the first spring) 60 which imparts a relatively downward elastic pressing force with respect to the front wheel 2 as described below, and the first compression spring ( The front axle case 20 supporting the front wheels 2 in a state that allows the expansion and contraction movement of 60 is configured to support the front wheels 2 in a vertical direction so as to be movable in a vertical direction.

As shown in Fig. 3, each of the left and right front wheels 2 is mounted to the front axle case 20 in which the front wheel drive device 21 is incorporated, so that the front wheel drive device 21 in the front axle case 20 is mounted. The steering wheel 16 is a driving wheel to which power is transmitted from, and the steering wheel 16 is steered over a predetermined angular range around the axis center Y of the center pin 23 by the tie rod 22 to which the rotation operation of the steering wheel 16 is transmitted. Consists of.

In the front wheel drive device 21, the output from the mission case 13 to which power from the engine E is transmitted is transmitted by the transverse transmission shaft 24 via a differential mechanism (outside the drawing). The bevel gears 23b and bevel gears provided on the front axle 25 are transferred to a vertical axis which serves as the center pin 23 via the bevel gears 24a and 23a. The driving force is transmitted to the front wheel 2 by the engagement of 25a).

The front axle case 20 is located between the upper case 20A fixed to the vehicle body frame 10 side, the lower case 20B fixed to the front wheel side, and the two cases 20A and 20B, The relative position with respect to the case 20A is comprised by the intermediate case 20C which changes position up and down.

As a result, the front axle 25 supported by the lower case 20B is supported such that the front axle 25 can be moved up and down within the range of the vertical length of the intermediate case 20C with respect to the upper case 20A, and the front wheel 2 It is possible to move up and down.

Moreover, in the front axle case 20, the 1st compression spring 60 which consists of a coil spring is mounted in the state wound around the said center pin 23, and this 1st compression spring 60 is the upper end side Upward movement is restricted by contacting the inner race of the bearing 20Aa for bevel gear 23a attached by fixing the upper and lower positions to the upper case 20A, and the lower end side is installed on the inner bottom of the intermediate case 20C. The thrust bearing 20Ca is contacted, and further downward movement is regulated, and it is comprised so that downward elastic pressing force may be given to the lower case 20B via the intermediate case 20C.

In addition, the bevel gear 23b installed at the lower end side of the center pin 23 is located below the bearing 20Ba fixed to the lower case 20B and is centered along with the vertical movement of the lower case 20B. It is fixed to the center pin 23 so that the up-down position of the pin 23 may be changed, and the center pin 23 is comprised so that the fall limit may be regulated by the fixing member 23c provided in the upper end part side.

The first compression spring 60 is configured to be in a compressed state at all times throughout the entire range of spring stretching stroke. By this structure, the elastic pressing force of the 1st compression spring 60 can be made to respond responsively over the whole range of stretching stroke.

3 shows that the first compression spring 60 is upward from the reference level L0 (corresponding to the reference level of each front wheel) at which the lower end of the first compression spring 60 is located in a state where the machine body is normally used. The upper limit level Lt which is compressed by the maximum allowable stroke S1 to the upper end and the lower end of the spring rises to the maximum (in this state, the upper end of the lower case 20B contacts the lower end of the upper case 20A and the lower case 20B). The rising of is stopped.] Is shown. That is, in this state, the upper end of the lower case 20B is in contact with the lower end of the upper case 20A and the ascending is stopped. On the contrary, the maximum allowable stroke S2 downward is the lower limit level Lb at which the reference level L0 and the first compression spring 60 are lowered as much as possible (this state is the fixing member 23c on the upper end of the center pin). Is in a state where the lowering stops in contact with the bearing 20Ab supporting the center pin 23 at the upper portion of the upper case 20A. The 1st compression spring 60 is comprised so that it may be in a compressed state always in the whole range of the spring expansion stroke.

As described above, when viewed from the reference level L0, the allowable stroke to the lower side is set larger than the upper side (that is, the one set to S1 &lt; S2) due to the rising ride of the front wheel 2 The allowable stroke range can be effectively suppressed for suppressing the excitation simulation caused by the shallow planting caused by the inclination of the main body of the machine by more actively suppressing the downward movement due to the depression of the front wheel 2 than the upper movement. To make it available.

[Rear wheel suspension structure by swinging support mechanism 7]

As shown in Figs. 4 to 6, each of the left and right rear wheels 3 is mounted to a pair of left and right rear axle cases 30 incorporating a rear wheel drive device 31, and the rear axle case 30. The power from the said 1st transmission shaft 14 is transmitted with respect to the rear wheel drive device 31 in ().

Power transmission from the first transmission shaft 14 to the rear wheel drive device 31 is left and right from the transverse rear wheel transmission shaft 32 and the rear wheel transmission shaft 32 linked to the first transmission shaft 14. And a pair of left and right side clutches 33 which respectively clamp down the power to the corresponding rear wheel drive device 31, wherein the power transmission structure is built into the rear rear axle case 34. The bosses 30A on the base end side of the left and right rear axle cases 30 are externally fitted to the cylindrical journals 34A formed on the left and right ends of the rear rear axle case 34, respectively. It is rotatably supported.

Although the said side clutch 33 is normally pressed by the spring 33a to the clutch on side, the shift member 33b which can be operated off is fitted to the rear wheel transmission shaft 32 of a horizontal direction, and the steering wheel ( It is linked with the operation member 33c which operates the said shift member 33b to the clutch off side so that transmission to the rear wheel 3 of a turning inside may be interrupted | cooperated with steering operation more than the predetermined angle of 16).

The rear wheel drive device 31 disposed in the rear axle case 30 transmits power to the rear axle 36 via the left and right gear type reduction mechanism 35 which decelerates and transmits to the corresponding rear wheel 3. It is comprised by the gear group provided in each of the said rear wheel transmission shaft 32, the said rear axle 36, and the relay shaft 37 provided between both shafts, and the rear axle case 30 of It is comprised so that it may move integrally with rotation.

The rear axle case 30 is pivotally rotated relative to the cylindrical journal 34A formed at each of the left and right ends of the rear axle case 34 so as to swing around the center of the transverse axis X along the machine body left and right directions. Although configured as possible, the swing support mechanism 7 for swinging the rear axle case 30 is configured as follows.

5 and 6, the rear axle case is fixed by fixing one end side of the upper support member 71 to the vertically rising wall portion 10A to which the lifting link 41 is attached at the rear portion of the vehicle body frame 10. As shown in FIG. Attach the lower support member 72 to the 30, and attach a second compression spring (an example of the second spring) 70 between the loose end side of these upper support members 71 and the lower support member 72. I wear it. The spring constant of the second compression spring 70 is set smaller than the spring constant of the first compression spring 60.

Reference numeral 73 in both figures is a center member provided between the upper support member 71 and the lower support member 72 to suppress bending of the second compression spring 70 and at the same time, the upper support member 71. The upper limit and the lower limit of the swing angle range of the rear axle case 30 are determined by the long hole 73A formed so as to be inserted into the shaft portion 71A provided on the loose end side.

The state shown in FIG. 5 has shown the standard position in the expansion direction of the 2nd compression spring 70 in the state in which a machine main body is normally used. The maximum allowable stroke S3 from this state to the upper side is the reference level L0 (corresponding to the reference position of the rear axle case, and also the rear wheel) indicated at the lower end of the second compression spring 70 in the figure, and the lower end thereof. Is the distance between the upper limit level Lt at which the position of maximally rises (this state is, for example, the coil spacing of the second compression spring 70 is lost). The maximum allowable stroke S4 downward is the lower limit level Lb at which the reference level L0 and the second compression spring 70 are lowered as much as possible (this state is the upper end of the long hole 73A of the center member 73). Side is in contact with the shaft portion 71A, and the lowering is stopped.

In this way, from the reference level L0, setting the allowable stroke to the upper side larger than the lower side (that is, setting S3 &gt; S4) is caused by the depression of the rear wheel 3 to the recessed portion. Allowing stroke to restrain the excitation of excitation caused by shallow planting caused by lifting of the rear of the machine main body by more actively suppressing upward movement by the tom of the rear wheel 3 than the downward movement. This is to ensure that the range can be used effectively.

In the shaft portion 71A provided on the loose end side of the upper support member 71, as shown in Fig. 6, the loose end side of the upper support member 71 is formed away from the vertically rising wall portion 10A. The center member 73 and the second compression spring 70 are mounted on the protruding end side of the shaft portion 71A to the machine main body transversely outward at two points separated from each other, and the fixing pin 74 of the shaft portion 71A. ), The second compression spring 70 can be removed together with the collar 75.

In addition, the lower support member 72 fixed to the rear axle case 30 by removing the fixing pin 76 or the circlip 79 at each end of the shaft portion 72A of the lower support member 72 ( 72, thereby removing the center member 73 itself. Therefore, when the center member 73 and the second compression spring 70 having different pressing forces or spring constants are alternately attached, the oscillating operation range of the rear axle case 30 is different. The swing performance can be set differently.

Moreover, it is suitable that the spring constant of the 2nd compression spring 70 is set smaller than the spring constant of the 1st compression spring 60 of the said telescopic support mechanism 6.

[Modification Example of First Embodiment]

(1) The front axle case 20 may be provided with a drive means 8 for changing the reference level L0 of the first compression spring 60 by driving the telescopic support mechanism 6.

As this drive means 8, a hydraulic apparatus can be used, for example as shown in FIG.

In this structure, the front axle case 20 is composed of an upper case 20A fixed to the vehicle body frame 10 side, and a lower case 20B fixed to the front wheel 2 side, and the upper case 20A. The lower case 20B is stretched up and down relative to the upper case, and the front axle 25 is moved relative to the upper case 20A in the up and down direction so that the height position of the front wheel 2 changes in the up and down direction. do.

In this structure, the spring pressing 23c fixed to the center pin upper end part and the upper case of the upper position of the center pin 23 are the 1st compression spring 60 for elastic compression which presses the center pin 23 downward. It is interposed between the piston 81 built in the cylinder chamber 80 integrally formed in 20A so that sliding is possible.

The cylinder chamber 80 is configured to supply pressure oil from a hydraulic source other than the drawing, and to set the position of the piston 81 at an appropriate height position. The set pressure of the pressurized oil supplied to the cylinder chamber 80 can be changed by operation of a pressure regulating valve, etc., not shown in the drawing. By changing the set pressure in this way, the height position of the piston 81 is changed to expand / extend the support mechanism ( Since the reference level itself by 6) can be changed, it is possible to change the reference level of the stretchable support mechanism 6 in accordance with, for example, a field site with a relatively shallow field or a field field with a deep field.

In addition, in the figure, reference numeral 20Ac denotes the inside of the upper case 20A so as to limit the maximum descending amount of the front axle 25 by the elastic support mechanism 6 by the contact of the fixing member 23c at the upper end of the center pin 23. It is a stopper formed integrally with the.

(2) As the drive means 8 which drives the expansion / extension support mechanism 6 of the front axle case 20, you may use an electric cylinder as shown in FIG.

In this structure, the electric cylinder is used instead of the hydraulic cylinder by using the front axle case 20 as in the case where the drive means 8 is constituted using the above-mentioned hydraulic apparatus.

Specifically, the piston type is performed by the screw shaft 84 which is driven to rotate in the forward and reverse directions by the electric motor 83 provided at the upper end of the upper case 20A. In the center of the member 82, a screw portion for screwing with the screw shaft 84 is formed to form a protrusion in the upper case 20A as a guide portion 85 for preventing rotation of the piston type member 82. The up-down position of the piston-type member 82 is adjusted via the screw shaft 84 by the drive force of the electric motor 83, and it is comprised so that the reference level of the expansion-contraction support mechanism 6 may be changed.

(3) A drive means 8 for driving the swing support mechanism 7 of the rear axle case 30 may be provided.

As shown in Fig. 9, the upper support member 71 is pivotably mounted about the horizontal support shaft 77 with respect to the vertically rising wall portion 10A provided at the rear portion of the vehicle body frame 10. The adjustment hydraulic cylinder 86 as the drive means 8 is provided in the edge part on the opposite side to the side in which the shaft part 71A on the loose end side of the member 71 was provided. The expansion and contraction of the adjusting hydraulic cylinder 86 causes the upper support member 71 to swing around the lateral support shaft 77 to change the attachment angle to the vertically rising wall portion 10A to the second compression spring 70. It is comprised so that the reference position of the oscillation support mechanism 7 can be changed by changing the support position of the upper end part side with respect to, and changing the up-down position of the rear axle 36 around the said horizontal axis center X.

Of course, it is also possible to employ an electric cylinder as the drive means 8.

(4) As a specific configuration of the swing support mechanism 7 that supports the rear axle case 30 so as to be swingable, as shown in FIG. 5, the loose end side and the lower support member 72 of the upper support member 71. It is not limited to what was comprised by the center material 73 provided across and the 2nd compression spring 70 externally inserted in the center material 73, For example, you may comprise as shown in FIG. .

In this structure, hook portions 70a are formed at both ends of the coil spring as the second compression spring 70, and the hook portions 70a are loosely end side of the upper supporting member 71 and the lower supporting member 72. Locked to the shaft portions 71A and 72A provided in each of them, the outer side of the coil spring penetrates through a cylindrical guide 78 that suppresses its bending. The cylindrical guide 78 is formed with a notch portion 78a that is elongated in the vertical direction so as not to interfere with the vertical movement of the shaft portion 71A which expands and contracts the second compression spring 70.

[2nd Embodiment]

In the swing support mechanism of the rear axle case according to the second embodiment, the first point is that the support point a of the up and down swing of the rear axle case is located at the front end of the support arm that protrudes forward from the rear axle case. It is different from the configuration of the form. Hereinafter, although it demonstrates concretely, about the member similar to previous embodiment, the same code | symbol is attached | subjected and description is not repeated.

Also in the riding type transfer machine according to the present embodiment, the front wheel 2 and the rear wheel 3 have a front wheel suspension structure by the elastic support mechanism 6 and a rear wheel suspension structure by the swing support mechanism 7. Each of these is suspended so that up-and-down displacement is possible.

[Front wheel suspension structure by telescopic support mechanism 6]

13 shows a front wheel suspension structure. As shown, the front wheels 2 are mounted on the front axle case 110, and the front axle case 110 has an upper case 110a fixed to the machine body side and a lower case fixed to the front wheel side ( 110b). Mainly, this front axle case 110 constitutes the expansion and contraction support mechanism 6 of this embodiment from the suspension spring 137 mentioned later.

Each upper case 110a is fitted with a lower case 110b that is rotatable about the longitudinal center P and slides in the longitudinal center P, and is fitted in the mission case 13. A differential shaft 132 extending from the differential mechanism on the left side, and a driven shaft 134 in which the upper axle 133 mounted on the lower case 110b is built into the upper case 110a, and the double bevel gear 135a. , 135b, 136a, and 136b are interlocked so that the front wheels 2 connected to the front axle 133 are driven. In addition, the vertical drive shaft 134 belongs to the lower case 110b side, and the vertical displacement of the vertical drive shaft 134 accompanied by the vertical displacement of the lower case 110b is such that the bevel gear 135b and the vertical drive shaft 134 Absorbed by a slide at the spline fit site. In addition, the said longitudinal axis center P is inclined a little back, and is called the caster angle (refer FIG. 10).

A suspension spring (an example of the first spring) 137 is inserted between the upper case 110a and the lower case 110b and inserted into the longitudinal drive shaft 134 and configured as a compression spring. The machine body load acting on the left and right front wheels 1 is elastically supported by the respective suspension springs 137.

The suspension spring 137 is configured to be in a compressed state at all times throughout the entire range of spring stretching stroke. By this structure, the elastic pressing force of the suspension spring 137 can be made to respond responsively over the whole range of stretching stroke.

Fig. 13 shows the maximum allowance of the suspension spring 137 upward from the reference level L0 (corresponding to the reference level of each front wheel) at which the lower end of the suspension spring 137 is located in the state where the machine body is normally used. Compressed by stroke S1 to move to the upper limit level Lt at which the lower end of the spring rises to the maximum (the upper end of the lower case 110b is in contact with the lower end of the upper case 110a and the ascending is stopped). Indicates. On the contrary, the maximum allowable stroke S2 downward is the lower limit level Lb at which the reference level L0 and the suspension spring 137 are lowered as much as possible (this state is the fixing member 134a on the upper end side of the driven shaft 134). ) Is in a stopped state in contact with the bevel gear 135b]. The suspension spring 137 is configured to always be in a compressed state over the entire range of the spring stretching stroke.

As described above, from the reference level L0, setting the allowable stroke to the lower side more than the upper side (that is, setting S1 <S2) is to increase the ride of the front wheel 2. The allowable stroke range is effective in suppressing the excitation simulation caused by shallow planting caused by the inclination of the front of the machine body by suppressing the downward movement caused by the depression of the front wheel 2 more than the upward movement by the upward movement. This is to make it possible to use it.

In addition, as shown in Fig. 17, the knuckle arms 140 are connected to the left and right lower cases 110b, and the knuckle arms 140 each have a tie rod 142 on the pitman arm 141 at the center of the machine body. Each of the front wheels 2 on the left and right sides is steered in the rotation operation direction by the rotation operation of the steering wheel 16.

[Rear wheel suspension structure by swinging support mechanism 7]

10 to 12 and 14 to 19, the swing support mechanism 7 is shown. As shown in the drawing, the rear axle case 115 journaling the left and right rear wheels 3 has a center case portion 115a through which shifting power extracted from the mission case 13 is input via the first transmission shaft 14. ) And a reduction case part 115b connected to both left and right ends thereof, and the center case part 115a and the left and right reduction case part 115b are connected to each other by a round pipe stay 117 to reinforce the whole case. It is. Support arms 151 extend and protrude forward from the brackets 150 connected to the left and right front surfaces of the center case portion 115a, and a band plate is provided on the inward side surfaces of the left and right reduction case portions 115b. A support link 152 formed by bending in an inverted U-shape is attached via a support pin 153 and protrudes upward.

The vehicle body frame 118 made of an angle pipe is connected from the mission case 13 toward the rear, and the support shaft (a) is connected to the vertical wall connecting portion 118a continuously provided in the front portion of the body frame 118. 154 is fixedly attached to the left and right horizontally, and the front end boss portion 151a of the support arm 151 which protrudes forward from the rear axle case 115 to both ends of the support shaft 154 is rubber. It is connected and supported via the bush 155. The rear axle case 115 supported in this manner swings up and down with the support of the shaft center a of the support shaft 154 at a position far away from the outer shape of the rear wheel 3 (outer side from the side). The entire rear axle case 115 can be tilted left and right by the elastic fusion of the rubber bush 155 while being displaceable.

Moreover, the support shaft 156 protrudes from the site | part which shifted to the right side of the center case part 115a in the rear axle case 115 to face forward, and was installed in the lower surface of the left side of the vehicle body frame 118. The support pin 158 protrudes toward the front of the kit 157, and boss portions 159a and 159b of the lateral rods 159 disposed in the transverse direction are connected to the support shaft 156. The lateral vibration of the rear axle case 115 is regulated by being connected via the rubber bush 160 over the support pin 158. In addition, a rubber stopper 161 is disposed on the left and right of the rear portion of the body frame 118, and the tilting range of the rear axle case 115 is brought into contact with the upper surface of the bracket 150 and the stopper 161. Are regulated.

In addition, at the rear of the body frame 118, a left and right pair of longitudinal frames 119 are installed to connect the front ends of the elevating links 41 formed of the four link mechanisms, and the horizontal frames 119 are arranged horizontally. Both ends of the support shaft 162 fixedly attached to the upper portion and the upper portion of the support link 152 protruding upward from the left and right sides of the rear axle case 115 are connected to each other through the long hole 163 in the vertical direction. Suspension springs (an example of the second spring) 164 configured to the compression springs are fitted to each support link 152 from the outside, and the machine body load acting on the left and right rear wheels 3 is left and right suspension springs. 164 is elastically supported.

In this case, the support point a when the rear wheel 3 journaled to the rear axle case 115 oscillates up and down falls farther forward than the outer shape of the rear wheel 3, and the rear wheel shaft center height is increased. Since it is at a height position close to, the vertical movement trajectory of the center of the rear wheel shaft is a circular arc trajectory with a large curvature near the vertical line. Therefore, even if the rear wheel 3 displaces large upwards, the displacement component of the front-back direction, especially the rear side is minute, and the rear wheel 3 which moved up was close to the mother implant apparatus 4 side, and the mother mount 45 The approach and contact of various mechanisms and parts arranged on the front side of the crest is avoided in advance.

The state shown in FIG. 14 has shown the standard position in the expansion direction of the suspension spring 164 in the state in which a machine main body is normally used. The maximum allowable stroke S3 from this state to the upper side is that the reference level L0 (corresponding to the reference position of the rear wheel) shown at the lower end of the suspension spring 164 in the figure, and the position of the lower end thereof rise to the maximum. The distance between the upper limit level Lt (this state is a state where the tilting (rolling) of the rear axle case 115 is restricted by the contact of the upper surface of the bracket 150 and the stopper 161). The maximum allowable stroke S4 downward is the lower limit level Lb at which the reference level L0 and the suspension spring 164 are lowered as much as possible (in this state, the upper end side of the long hole 163 in the vertical direction is supported by the support shaft). 162 is in contact with the descending stop state].

As described above, from the reference level L0, setting the allowable stroke to the upper side larger than the lower side (that is, setting S3> S4) is caused by the depression of the rear wheel 3 to the recessed portion. The allowable stroke range is suppressed to suppress the excitation of the planting caused by shallow planting caused by lifting of the rear side of the machine body by more actively suppressing upward movement due to the tom of the rear wheel 3 than the downward movement. This is to make effective use.

In addition, when the suspension spring 164 with different pressing force or spring constant is changed and attached, the swinging operation range and the swinging performance of the rear axle case 115 can be set differently. In addition, it is preferable that the spring constant of the suspension spring 164 is set smaller than the spring constant of the suspension spring 137 of the elastic support mechanism 6.

18 and 19 show the internal structure of the rear axle case 115. In the center case portion 115a of the rear axle case 115, an input shaft 170 to which power from the mission case 13 is transmitted is mounted to the front, and a transverse direction bevel gear-linked to the input shaft 170. The transmission shaft 171 spans horizontally, and the power transmitted to the lateral transmission shaft 171 branches left and right through the side clutch 172, the gear reduction mechanism 173, and the rear axle 174. It is supposed to be transmitted to the rear wheel 3. That is, the axis center of the transverse transmission shaft 171 becomes the power split line b with respect to the left and right rear wheels 3, and this power split line b is located inside the rear wheel outline from the side of the machine body. It extends and protrudes (see FIG. 11).

As shown in Figs. 18 to 20, the side clutch 172 has a clutch gear 175 loosely fitted to the transverse transmission shaft 171, and a clutch sleeve fitted outside the spline to the transverse transmission shaft 171. 176 and a clutch on pressing spring 177 inserted into the transverse transmission shaft 171 so as to slide the clutch sleeve 176 toward the case center side, and the clutch gear 175 is extended. Clutch-on which transfers the power of the transverse transmission shaft 171 to the clutch gear 175 by engaging the hook portion 175b provided on the boss portion 175a and the hook portion 176a provided by the clutch sleeve 176. A condition is brought about, and the clutch sleeve 176 is shifted outward against the spring 177 to release the engagement of the hook portions 175b and 176a, thereby driving the power from the lateral transmission shaft 171 to the clutch gear 175. Clutch off state to block delivery in seconds It is possible.

Moreover, the transmission in the deceleration state is enabled on the lower side of the transmission of this side clutch 172 by the clutch operation continuously pulled by a clutch off operation. That is, the reduction gear drive 178 smaller in diameter than the clutch gear 175 is rotatably mounted on the lateral transmission shaft 171, and the clutch gear (178) is extended to the extension boss portion 178 a of the gear 178. 175 is loosely fitted, and the hook part 178b formed in the inner end part of the extension boss part 178a, and the hook part 176b formed in the outer end surface of the clutch sleeve 176 oppose. Therefore, when the clutch sleeve 176 is further shifted outward from the clutch off position against the spring 177, the hook portions 176b and 178b engage with the power of the transverse transmission shaft 171 to reduce the power transmission gear 178. ), And the rear wheel 3 is decelerated than the normal clutch on state and driven.

The inner end of the clutch sleeve 176 is disposed against the relay sleeve 180 shifted by rotation of the operation shaft 179 mounted to the central case portion 115a, and is disposed outside the case of the operation shaft 179. The clutch sleeve 176 is shifted against the spring 177 by rotating the clutch operation lever 181 provided at the end toward the front, and the &quot; clutch on state &quot; shown in FIG. The "clutch off state" shown in (b) of FIG. 2 and the "deceleration transmission state" shown in (c) of FIG. 20 are shown in order.

In addition, the clutch control lever 181 is to be automatically operated in conjunction with the front wheel steering operation. That is, as shown in Fig. 18, the rear end bracket 182a of the training rod 182 that protrudes backward from the left and right of the pitman arm 141 passes through the long hole 183 and the connecting pin 184. It is linked to the clutch operation lever 181 on either side. Therefore, when the pitman arm 141 is rocked from the straight position to the set angle or more and the front wheel 2 is steered to the left side or the right side over the set angle (for example, 30 °), the rear wheel becomes the turning inside. The clutch operation lever 181 to (3) rotates forward by the operation rod 182 which pulls forward, and the side clutch 172 of the turning inner side is switched to said "clutch off state", and the traveling machine The main body 1 quickly turns to the three-wheel drive state of the steered left and right front wheels 2 and the turning rear wheels 3, and when the front wheels 2 are steered larger to reach the limit, the clutch operating lever 181 is rotated further forward to cause the above "deceleration transmission state" so that the traveling machine main body 1 is steered by the left and right front wheels 2, the rear wheels 3 of the turning outside, and the deceleration-driven turning. In the four-wheel drive state of the rear wheel (3) inside Lee wheels.

[Modification Example of Second Embodiment]

This invention can also be implemented with the following forms.

(1) Although not shown, the side rod 159 may be hypothesized over the portion of the back of the support arm 151 and the vehicle body frame 118.

(2) In 2nd Embodiment, a pair of right and left support arms 151 protrude forward from the rear axle case 115 which journaled the left and right rear wheels 3, and the front support point a Although the case where the support was able to swing up and down and tilted in the left and right direction was illustrated as an example, one support arm 151 having a large rigidity protrudes forward from the rear axle case 115, and the front end boss portion thereof. 151a may be connected to the support shaft 154 via a rubber bush 155.

(3) The suspension spring 164 for elastically supporting the rear axle case 115 can be implemented in such a manner as to act on the center portion of the case with a large diameter.

(4) As a means for limiting unnecessary lateral movement of the rear axle case 115 and the support arm 151, in addition to using the side rod 159, a contact-type lateral movement restricting guide member is placed in place such as a suspension spring mounting portion. It is also possible to adopt a structure to arrange.

(5) In any of the first and second embodiments, the front wheel suspension structure was configured such that the front wheels were movable up and down by linear expansion and contraction of the expansion and contraction support mechanism 6. Instead of this, mechanisms such as the swing support mechanisms 7 of the two embodiments may be employed, and the front wheels may be configured to be movable up and down by non-linear expansion and contraction.

[Third Embodiment]

Hereinafter, although 3rd Embodiment of this invention is described, about the same member as the previous embodiment, the same code | symbol is attached | subjected and description is not repeated. In addition, in this embodiment, the side clutch is arrange | positioned in the longitudinal deceleration case part instead of a lateral case part among the rear axle cases.

As shown in FIGS. 22 to 24, the rear axle case 210 for driving the rear wheels is a transverse rear axle supported by the body frame 10 in a predetermined range around the front and rear axis center R in a rollable manner. It is comprised by 210 A of case parts, and the deceleration case part 210B connected to each of the left and right both ends. In the transverse rear axle case portion 210A, a transverse transmission shaft 241 for dividing the power from the first transmission shaft 14 protruding to the rear from the mission case 13 to the left and right is built in the transverse rear axle case portion 210A. 1 Bevel gear interlocked with the transmission shaft (14). In addition, each reduction case portion 210B has a rear axle 242 journaling the rear wheels 3, and a reduction gear mechanism 243 that slows and interlocks the lateral transmission shaft 241 and the rear axle 242. Is equipped.

A frictional side clutch 245 for intermittent transmission of power to the rear wheels 3 is interposed between both ends of the lateral transmission shaft 241 and each reduction gear mechanism 243. These side clutches 245 are splined to the transverse transmission shaft 241 and are integrally rotated, and the boss member 246 which is movable in the axial center direction and the driven drum 247 which interlocks with the reduction gear mechanism 243. And the frictional interlocking operation (clutch-on) by the movement of the boss member 246 to the machine body transversely outward, and at the same time, the frictional interlocking release is released by the boss member movement to the machine main body transversely inner side (clutch-off). A plurality of friction plates 248 are alternately coupled to the boss member 246 and the driven drum 247 so that the clutch spring 249 for pressing and moving the boss member 246 to the clutch on side is transversely driven. 241 is externally fitted to the structure.

23 to 24, a brake 250 for stopping the machine main body is provided between the deceleration case portion 210B on the right side and the boss member 246 on the right side clutch 245. As shown in FIG. The brake 250 is press-bonded to the outer circumference of the boss member 246 by a friction plate 251 fitted with a spline outer fitting and an inner circumference of the deceleration case portion 210B to press the rotationally stopped friction plate 252. 246 and the transverse transmission shaft 241 integrally rotating therewith, and the friction plate 251, 252 is moved by moving the cup-shaped operation member 253 loosely fitted to the boss member 246 laterally outside the machine body. They are to be pressed together.

The brake 250 for stopping the main body of the machine is operated by a brake operating shaft 254 rotatably mounted on the upper surface of the reduction case 210B around the longitudinal center P1. That is, the shift fork 255 is attached to the inrush portion of the case of the brake operation shaft 254, and the shift fork 255 is disposed opposite to the end surface of the operation member 253, and the brake operation shaft ( By rotating the 254, the operation member 253 can be shifted via the shift fork 255 to brake the boss member 246.

And, as shown in FIG. 24, the operation lever 254a provided in the case outer protrusion part of the said brake operation shaft 254 is linked with the pedal 56 arrange | positioned at the right front of the foot of the boarding part in a drive part. 257 is interlocked and connected, the linkage rod 257 is tension-displaced forward with the depression operation of the pedal 56, and the brake 250 is braked, and the brake 250 is braked by releasing the depression. It is supposed to be released. Further, by holding the pedal 56 operated by the depression operation with the lock lever 58 (Fig. 2), the parking state can be caused. In addition, although the detailed structure is abbreviate | omitted, the left end part of the support shaft 56a which connected the pedal 56 is mechanically linked to the operation system of the hydrostatic stepless speed changer (an example of a continuously variable transmission) 12, and the pedal 56 ), The main shift lever 232 (Fig. 21), which is operated in the forward area or the reverse area, is forcibly returned to the neutral stop position.

The operation structure of the side clutch 245 is configured as follows. That is, the clutch operation sleeve 261 which is disposed against the end face of the boss member 246 via the thrust collar 260 is slidably inserted into the transverse transmission shaft 241 and at the same time, the deceleration case portion 210B is provided. The clutch operating shaft 262 is rotatably mounted around the longitudinal center P2 on the upper surface of the upper surface, and the eccentric cam 263 formed at the indentation end of the case of the clutch operating shaft 262 is the clutch operation sleeve. It is arrange | positioned facing the end surface of 261, and the side clutch 245 is made to be on-off operation by the rotation operation of the clutch operation shaft 262. As shown in FIG. In addition, as shown in Fig. 22, the clutch operation shaft 262 of the side clutch 245 on the left side is clutched off by counterclockwise rotation, and the clutch on state is maintained during clockwise rotation. Further, as shown in Fig. 22, the clutch operation shaft 262 of the side clutch 245 on the right side is clutched off by clockwise rotation in plan view, and the clutch on state is maintained in the counterclockwise rotation. The phase of the eccentric cam 263 is set as much as possible.

Then, only the side clutch 245 inside the swing is automatically turned off in conjunction with the steering operation of the front wheels 2 at a set angle or more from the straight position, so that the machine according to the difference in the propulsion ability of the left and right rear wheels 3 is obtained. The automatic steering mechanism A which brings about a main body turning force is provided, and the specific structure of the automatic steering mechanism A is demonstrated below.

As shown in FIG. 24, the pitman arm 265 oscillated from side to side around the longitudinal axis Z by the rotation operation of the steering wheel 16, and the knuckle arm 266 of each of the front wheels 2 are provided. The steering mechanism 268 is interlocked through the tie rods 267 to form the steering mechanism 268, and the vertical axis center is provided at the lower portion near the front and rear middle parts of the machine body and the operation bracket 265a continuously installed on the pitman arm 265. The intermediate arm 269 which is pivotally arranged around (S) is interlocked and connected by a push rod 270, and the intermediate arm 271 which swings flatly around the longitudinal axis center S integrally with the relay arm 269. It is provided. The left and right ends of the intermediate arm 271 and the operation lever 262a continuously provided on the case outer protrusion of the clutch operation shaft 262 are linked to each other via a rod 272 as an interlocking member.

In addition, the rod 272 and the operation lever 262a are flexibly connected through the elongated hole 273 formed in the rear bracket 272a of the rod 272 and the connecting pin 274 of the operation lever 262a. When the rod 272 is pulled forward greatly, the connecting pin 274 is pressed at the rear end of the long hole 273 so that the operation lever 262a is rotated in the clutch off direction, and the rod 272 is rotated. The long hole 273 only moves back with respect to the connection pin 274, even if it pushes back and it is comprised so that the operation lever 262a may not be rotated.

According to the above configuration, the steering angle of the front wheels 2 in the normal transplantation operation is smaller than the set angle, and the hole is long even when the intermediate arm 271 swings and one rod 272 is pulled forward. Only the movement of the 273 and the connecting pin 274 relative to the operation lever 262a does not rotate the operation, the left and right side clutches 245 are kept in the on state, and the left and right rear wheels 3 are at the same speed. Driven by.

If the front wheels 2 are steered largely above the set angle on the left or right side to change the direction of the machine body in the vicinity of the paddy field, one rod 272 will be pulled forward beyond the ridge of the long hole 273. The operation lever 262a of the side clutch 245 corresponding to the turning inside is rotated in the clutch off direction. As a result, the main body rotates by the three-wheel drive of the left and right front wheels 2 and the right rear wheels 3 which are turning outwards, and the rear wheels 3 in the turning inner side in which the side clutch 245 is turned off It can be grounded and passed along with the turning movement of the machine main body, and the machine main body can be rotated without unduly desolating the field site by the rear wheel 3 inside the turning.

Although the above structure and function are the same as the conventional automatic steering mechanism (for example, refer Unexamined-Japanese-Patent No. 2002-264835), the following structures are added to this invention.

As shown in Figs. 24 and 25, the front end of each rod 272 which interlocks the both ends of the intermediate arm 271 and the operation lever 262a of the side clutch 245 is provided as an actuator for side clutch on-off. The single movable hydraulic cylinder 281 is connected via the front bracket 272b.

The hydraulic cylinder 281 is configured to be short-actuated when the hydraulic oil is supplied, and to be extended by the built-in spring 283 when the hydraulic oil is supplied, and as shown in the hydraulic circuit diagram of FIG. 26 via an electronic control valve 284. It is intended to be controlled operation. In Fig. 26, reference numeral 285 denotes a torque generator for power steering, and reference numeral 286 denotes an electronic control valve and assembly that is in charge of the operation of the hydraulic cylinder 5 for lifting.

24 to 26, the control valve 284 is normally in the non-excited state, and both hydraulic cylinders 281 are in a single-axis operation state under pressure oil supply, including the hydraulic cylinders 281 at this time. The linkage length of the rod 272 is in the standard state. Then, in this standard state, when the front wheel 2 is steered from the straight position to the set angle θ ₀ (eg, 30 °) or more, the side clutch 245 of the rear wheel 3 of the turning inner side as described above. ) Is automatically turned off.

Then, the control valve 284 is operated and controlled as follows via the control device 287. That is, steering angle (theta) from the straight position of the front wheel 2 is detected by the steering sensor 288 which consists of a potentiometer, a rotary encoder, etc., is input to the control apparatus 287, and the front wheel 2 When it is detected from the straight position that the steering angle is greater than or _equal to the set angle θ ₀ , the control valve 284 intermittently has a period T for a predetermined time t as shown in FIG. 25 (b). While the energization is controlled and the control valve 284 is energized and switched, both hydraulic cylinders 281 are drained and extended to the built-in spring 283 to lengthen the linkage length of both rods 272.

In this case, one of the rods is pulled forward in response to the steering of the front wheel 2 at a set angle or more and the side clutch 245 of the turning inner side is turned off. Since the rod 272 is displaced rearward as long as it is energized and the linkage length of the rod 272 becomes long, the side clutch 245 of the turning inner side which was turned off returns to an on state. When the energizing excitation of the control valve 284 is stopped and the hydraulic cylinder 281 is shortened, and the linking length of the rod 272 is shortened to a standard state, the side clutches 245 inside the turning are turned off again. With the intermittent excitation of the control valve 284, the side clutch 245 inside the swing is intermittently turned off by a predetermined time a (= T − t) at a predetermined period T.

Moreover, although the rod 272 which operates the side clutch 245 in the rear wheel 3 of the turning outer side by the intermittent operation of the control valve 284 will change a linkage length similarly, this change will be made with a long hole ( Since it is absorbed by the fusion of 273 and is not transmitted to the operation lever 262a, the side clutch 245 outside the swing is kept in the on state.

The pattern which intermittently energizes the control valve 284 and intermittently turns on and off the side clutch 245 of the rear wheel 3 of a turning inside is considered various, and some of them are shown below.

[First Example]: As shown in Fig. 27A, the steering angle θ of the front wheel 2 is the maximum steering angle from the set angle θ _{0 at} which the automatic steering mechanism A is activated. In the entire area up to (theta) m, the control valve 284 is given a predetermined clutch off time a ₁ at a constant period T.

[Second example]: As shown in Fig. 27B, the steering angle θ of the front wheel 2 is the maximum steering angle from the set angle θ _{0 at} which the automatic steering mechanism A is activated. in the entire region fingers (θm) how, at regular cycles (T) at the same time to impart a predetermined clutch-off period (a _1), in the stroke to return the front wheel 2 in the straight, and the predetermined angle (θ ₀ The excitation is stopped at a set angle θ ₁ greater than) to quickly turn on the side clutch 245 inside the swing.

[Third example]: As shown in Fig. 27C, the steering angle θ of the front wheel 2 is larger than the set angle θ _{0 at} which the automatic steering mechanism A is activated. In the operation region up to the first setting angle θ ₁ , a predetermined clutch off time a ₁ is given for every constant period T, and the second setting angle θ ₂ larger than the first setting angle θ ₁ is provided. In the operation region up to, the predetermined clutch off time a ₂ is greater than the clutch off time a _{1 for} each cycle T, and the maximum steering angle θ m is obtained from the second set angle θ ₁ . In the operation region up to, a predetermined clutch off time a ₃ is given for each of the cycles T greater than the clutch off time a ₂ .

That is, as the front wheel steering angle increases, the average clutch off time increases in stages, thereby increasing the turning function.

[Fourth Example]: As shown in Fig. 27D, the steering angle θ of the front wheel 2 is the maximum steering angle from the set angle θ _{0 at} which the automatic steering mechanism A is activated. In the entire area up to (theta) m, the clutch off time a given for each constant period T is continuously increased and changed linearly. As a result, the larger the front wheel steering angle, the longer the average clutch off time, and the smaller the turning function becomes.

[Fifth example]: As shown in Fig. 27E, the steering angle θ of the front wheel 2 is the maximum steering angle from the set angle θ _{0 at} which the automatic steering mechanism A is activated. In the region up to an angle θ _{2 which} is slightly smaller than θ m, the clutch off time a given every fixed period T is continuously and linearly increased and changed from this angle θ ₂ to the maximum steering angle θ m. In the operation region up to), a predetermined clutch off time a ₁ is given at a predetermined period T, and the front maximum steering angle (in the stroke for returning the front wheel 2 straight from the maximum steering angle θ m) is The clutch off time (a) given immediately at a constant period (T) is changed continuously and linearly from θm immediately, and the excitation is stopped at a set angle (θ ₁ ) larger than the set angle (θ ₀ ) to quickly turn inside. Side clutch 245 to be inserted.

[Sixth Example]: As shown in Fig. 27F, the steering angle θ of the front wheel 2 is the maximum steering angle from the set angle θ _{0 at} which the automatic steering mechanism A is activated. In the entire area up to (theta) m, the clutch-off time (a) given every fixed period (T) is continuously and nonlinearly increased and changed to be the clutch-off time (a ₁ ) at the maximum steering angle (theta) m. As a result, the larger the front wheel steering angle θm, the longer the average clutch off time a becomes, and the smaller turning function rapidly increases.

In addition, in the case where the expansion and contraction of the hydraulic cylinder 281 becomes impossible due to the failure of the electric control system or the like, the connection position between the front bracket 272b and the hydraulic cylinder of the rod 272 is adjusted to include the hydraulic cylinder. By making the linkage length of the rod 272 a standard length, the automatic steering mechanism A can be operated, and when the front wheel steering angle becomes _equal to or greater than the set angle θ ₀ , the side clutch of the rear wheel 3 of the turning inner side ( 245 can be turned off continuously (see FIG. 24).

[Modification Example of Third Embodiment]

This invention can also be implemented with the following forms.

(1) In the above embodiment, a pair of hydraulic cylinders 281 assembled to a rod 272 which interlocks both ends of the intermediate arm 271 and the left and right side clutches 245 are connected to a single control valve 284. Although both hydraulic cylinders 281 are operated in the same direction at the same time, the hydraulic cylinder on the side where the side clutch 245 is turned off by intermittently operating the three-position switching control valve between the neutral position and one of the switching positions. Only 281 may be operated intermittently.

(2) In the above embodiment, the hydraulic cylinders 281 serving as the side clutch intermittent on / off actuators are respectively assembled in a pair of rod interlocking systems for interlocking the intermediate arm 271 and the left and right side clutches 245. An actuator such as a hydraulic cylinder that can be switched to three positions of neutral, short axis, and elongation is assembled in a rod linkage system linking the pitman arm 265 and the relay arm 269, and the pressure rod 270 is pushed backwards. During the left turn, the neutral side and the short axis are operated repeatedly by the actuator, and the left side clutch 245 is intermittently turned on and off, and during the right turn to operate the pull rod 270 forward, the neutral and the elongation are repeated. By operating, the right side clutch 245 can be intermittently turned on and off.

(3) In the above embodiment, by changing the constant period T clutch off time a stepwise or continuously as described above, as the front wheel steering angle θ becomes larger, the average clutch off time becomes longer and turns smaller. Although the turning function is gradually increased, one clutch off time (a) is made constant, and as the front wheel steering angle (θ) is increased, the period (T) is changed so as to be smaller stepwise or continuously and within a predetermined time. It is also possible to lengthen the average clutch off time at.

(4) Although the above embodiment exemplifies a mode in which one side clutch 245 intermittently is turned off while giving a speed difference to the left and right rear wheels 3 to exhibit a turning function, the side is intermittently turned off. It is also possible to carry out in the form of braking operation of the side brake following the off operation of the clutch.

(5) In the above embodiment, when the front wheel 2 is steered at a set angle θ ₀ or more, the automatic steering mechanism A which automatically turns off the side clutch 245 with respect to the rear wheel 3 inside the swing. ) Is mechanically configured and one side clutch 245 intermittently turned on by the automatic steering mechanism A is turned on intermittently, but the left and right side clutches 245 are each independently operated only by an actuator. It is configured so as to be on-off operation and intermittently on the side clutch 245 with the desired characteristic by operating only one actuator in association with the front wheel steering of a set angle (θ ₀ ) or more. It can also be controlled off.

(6) Although the rod 272 is used as an interlocking member for interlockingly connecting the operation lever 262a of the intermediate arm 271 and the side clutch 245 in the above embodiment, a wire may be used as the interlocking member.

(7) As an actuator for intermittently turning on and off the side clutch 245 operated by the operation of the automatic steering mechanism A, a hydraulic cylinder 281 operated and controlled by the control valve 284 as described above is used. In addition, an electric actuator such as an electric cylinder or an electromagnetic solenoid controlled directly by the control device 287 can be used.

[Other related]

As mentioned above, although each embodiment demonstrated the riding type electric machine as an example, this invention is applicable also to other riding type munon working machines, such as a sowing machine and a transplanting machine.

By such a configuration, the present invention provides a riding type munon working machine that can exhibit high-speed running smoothly in a field by exerting a suspension function on the front wheel and the rear wheel.

Claims (12)

It is a passenger-type non-non-working machine having a front wheel (2) supported on the front axle case (110) and a rear wheel (3) supported on the rear axle case (115), An elastic support mechanism (6) capable of independently suspending the front wheels (2) and moving them vertically; It is provided with the oscillation support mechanism 7 which can rock the said rear wheel 3 to an up-down direction about the horizontal axis center a along a machine body left-right direction, The rear axle case 115 is provided as a single case member, and each rear wheel 3 is mounted and supported by this single case member, The horizontal axis center a of the swing support mechanism 7 extends through the front end of the support arm 151 which protrudes forward from the rear axle case 115, The rear axle case (115) is supported by the traveling machine main body (1) so as to be able to swing up and down with the horizontal axis center (a) as a supporting point. delete delete delete The first and second springs 137 of claim 1, wherein each of the front wheels 2 is elastically supported on the elastic support mechanism 6 so as to be capable of being vertically displaced independently of each other. And a second spring (164) for elastically supporting the rear axle case (115) in the swing support mechanism (7). The riding type non-non-working machine according to claim 1 or 5, wherein restriction means for limiting lateral movement of the rear axle case (115) is provided. The support arm 151 is provided on the swing support mechanism 7 in a pair of right and left, and a suspension spring 164 for elastically supporting the rear axle case 115 is provided. And said regulating means comprises a side rod (159) arranged between said rear axle case (115) or support arm (151) and a body frame (118). delete delete delete delete The support shaft (1) according to claim 1, wherein a pair of right and left support arms (151) are provided on the swing support mechanism (7), and the horizontal axis (a) connects the front ends of these support arms (151) ( And 154).

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