KR20030066524A - Passenger type paddy field tiller - Google Patents

Abstract

A swivel faucet work machine that is capable of turning lightly without depleting the paddy field and at the same time excellent in operability at the time of stopping the gas, while simplifying the structure of the traveling system. For this purpose, a boss member 96A for supporting the drive side friction plate of the side clutch 96 is mounted to the left and right of the lateral transmission shaft 92 provided in the rear axle case 10, and the boss member 96A. And the side clutch 96 are connected and disconnected, and the gas stop brake 99 is provided only in the boss portion 96A of one side clutch 96. The gas stop brake 99 is composed of a friction plate 99a on the rotational side which is integrally rotatable with the boss member, and a friction plate 99b on the fixed side which is held in engagement with the rear axle case in a non-rotative manner. In conjunction with the pedal step operation, the lateral friction plate 99a and the fixed friction plate 99b are pressed against each other to brake the lateral transmission shaft 92.

Description

Riding type faucet work machine {PASSENGER TYPE PADDY FIELD TILLER}

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a riding type power receiver that is configured to transmit shifted power to front and rear steerable wheels and rear and rear steerable wheels.

BACKGROUND OF THE INVENTION In a rice transplanter, which is a representative of a riding faucet working machine, a wheel driving type that drives both front and rear wheels at a constant speed through a differential mechanism and drives the rear and rear wheels at constant speed through a side clutch and brake is widely used. As the operation structure, for example, the main clutch pedal for intermittent operation of the power transmission from the engine to the transmission transmission is arranged at the left side of the foot of the driver, and the side clutch / brake is independently operated at the right of the foot of the driver. A pair of left and right side clutch brake pedals are arranged in parallel.

In the above configuration, by stopping the main clutch pedal by pressing the main clutch pedal and simultaneously pressing the left and right side clutch brake pedals, the left and right side clutches are blocked, and the left and right side brakes are braked to perform the gas stop. Can be. In addition, by steering the front wheels and stepping on only one side clutch brake pedal to be inside the swing, by clutching the side clutch inside the swing and braking the side brake inside the swing, (小 旋回) can be.

Also in the work machine which enters a faucet, if it is comprised so that a left and right rear wheel may be driven through the differential mechanism similarly to a tractor, the drive speed of a left and right rear wheel will be changed automatically at the time of turning, and smooth turning driving can be performed. However, in a faucet where irregularities are present on the surface and the ground loads of the left and right rear wheels are easily changed, the rotational speeds of the left and right sides change depending on the load, so that the straightness decreases and gas steering becomes difficult. Therefore, the rear wheel side clutch and brake system is adopted in faucet machines such as rice transplanters, where straightness is important.

The riding type faucet working machine provided with the traveling system of the above structure is suitable for running in a faucet because of its excellent straight running ability. However, there were the following problems in the turnability in the rice paddies.

That is, in the case of a large U-turn turning of the body in the paddy field, when the gas turning is performed by operating the side clutch brake pedal, the rear wheels inside the swing are fixed by the side brakes, and thus the rear wheels that do not rotate are attracted and turned. As a result, it was easy to cause a large ruin of the paddy field or an increase in running load. Especially in deep rice fields, this tendency was large.

In order to stop the gas, the main clutch pedals arranged on the left side of the foot and the left and right side clutch brake pedals arranged on the right side of the foot are stepped on. However, since three pedal stepping operations were necessary, the operation was cumbersome. In particular, since the left and right side clutch brake pedals must be stepped on at the same time, a mechanism for connecting both side clutch brake pedals with a connecting bracket is required separately in the case of road running. In addition, there is a problem that a change operation of the connecting brackets is required in accordance with the running in the paddy field and the running out of the paddy field, and the operation is cumbersome.

SUMMARY OF THE INVENTION The present invention has been made in view of such a situation, and it is possible to lightly turn without depleting the rice paddy while simplifying the structure of the traveling system, and operability at the time of gas turning and gas stopping. An object of the present invention is to provide an excellent riding type power receiver.

1 is an overall side view of a rice transplanter;

2 is an overall plan view of a rice transplanter;

3 is a side view of the whole body;

4 is a plan view of the whole body;

5 is a rear view showing a drive structure of the fertilizing device.

6 is a longitudinal side view showing a rolling support structure of a drive case and a rear axle case for the fertilizer device;

7 is a longitudinal sectional side view showing an attachment structure of a rolling spring;

8 is a vertical rear view showing the attachment structure of the rolling spring;

Fig. 9 is a transverse plan view showing a transmission structure in a drive case for a fertilizer device;

10 is a side view showing a conventional connection structure between the propeller shaft and the input shaft of the rear axle case;

11 is a plan view showing an operation structure of the main clutch brake and the side clutch;

12 is a sectional view showing a transmission structure;

13 is a sectional view showing a planting gear mechanism;

Fig. 14 is a sectional view showing a structure in a longitudinal case supporting the rear wheels;

Fig. 15 is a sectional view showing a structure in a longitudinal case supporting the rear wheels;

FIG. 16 is a side view showing another embodiment of the rolling spring bearing; FIG.

Fig. 17 is a perspective view of a main part showing the arrangement of a gas stop pedal (main clutch brake pedal) in another embodiment;

(Explanation of symbols for the main parts of the drawing)

One; Front wheel 2; Rear wheel

10; Rear axle case 13; Boarding unit

92; Lateral drive shaft 96; Side clutch

99; Gas stop brake A; Yawing Jersey Organization

CBP; Gas stop pedal

In order to achieve the above object, the passenger-type power receiving work machine according to the present invention, as described in claim 1, to transmit the shifted power to the front and rear wheels 1 of free steering and the rear wheels 2 of non-steering and free steering. In the above-mentioned riding type power faucet, the left and right rear wheels are provided with a pair of left and right friction type side clutches 96 for inserting and stopping power transmission for each rear wheel, and these rear wheels are axially supported by the rear axle case 10. The side clutch 96 located inside the swing by steering operation of the left and right front wheels 1 by the steering wheel 14 and at the same time by operating the gas stop pedal CBP. In a passenger type power receiving machine equipped with an actuated gas stop brake (99), the rear axle case (10) is connected to the lateral transmission case part (93) and the left and right ends of the lateral transmission case part, respectively. The side clutch 96 is provided in the reduction case part 95 while the gas stop brake 99 is installed in the reduction case part 95. In the rear axle case 10, a clutch linkage rod 116 for operating the respective side clutches 96 and a brake linkage rod 110 for operating the gas stop brake 99 extend and are installed. The clutch operation shaft 104 operated by the clutch linkage rod 116 and the brake operation shaft 100 operated by the brake linkage rod 110 protrude in the one reduction gear case 95. It is characterized by that.

In addition, the present invention is characterized in that a shift fork 101 for operating the gas stop brake 99 is provided at the inrush portion of the brake operation shaft 100 into the rear axle case 10.

In the present invention, the shift fork 101 is arranged to face the end face of the operation member 98 for operating the gas stop brake 99, and the shift fork is rotated while the brake operation shaft 100 is rotated. As the operating member 98 is shifted through 101, the gas stop brake 99 is configured to be braked.

The present invention is characterized in that an eccentric cam (105) for operating the side clutch (96) is provided at the inrush portion of the clutch operation shaft (104) into the rear axle case (10).

In the present invention, the side clutch operation shaft 104 is mounted through the upper surface of the one speed reduction case portion 95, and the lower end portion thereof is provided in a support hole formed below the speed reduction case portion 95. It is characterized in that it is supported.

Other features, operations, and effects of the riding type faucet according to the present invention will become apparent by reading the preferred embodiments of the present invention described below with reference to the accompanying drawings.

(Description of a Preferred Embodiment)

EMBODIMENT OF THE INVENTION Hereinafter, the preferred embodiment of this invention is described with reference to drawings.

1 and 2, a riding type rice transplanter having a six-row planting specification is shown as an example of a faucet working machine. This riding type rice transplanter is a rear-mounted self-propelled gas body 3 equipped with a pair of free steering wheels 1 and a non-steerable left and right rear wheels 2, which has a planting apparatus 4 of 6 sets of planting specifications. The elevating free passage is connected via four link mechanisms 5 driven by the elevating cylinder 6, and at the same time, the fertilizing apparatus 7 of six irradiation amounts is provided at the rear of the body.

As shown in FIGS. 1 to 4, a transmission case 9 having a front axle case 8 for supporting the front wheels 1 is provided in all of the body frames 39 of the self-propelled gas 3. The connection is fixed. At the rear of the base frame 39, a rear axle case 10 for supporting the rear wheels 2 is supported by a rolling free path. In the vicinity of the front of the transmission case 9, the engine 11 having the output shaft 11a in the lateral direction is mounted via the anti-vibration rubber 12. The engine 11 is covered with the engine bonnet H which consists of the whole bonnet HF and the rear bonnet HR, and the boarding drive part 13 is arranged and arranged behind the engine bonnet H. As shown in FIG. The boarding driver 13 is provided with a steering wheel 14, a driver's seat 15, a driving step S and the like for steering the front wheel 1. The driving step S is arranged above the transmission case 9.

The seedling device 4 is a set of six types of rotary type that is placed in the paddy field by cutting the seedlings from the lower end of the seedling stand 16 for one week from the lower end of the seedling stand 16 by placing six sets of hairs and reciprocating the set stroke in the left and right directions. The planting mechanism 17, the three stop floats 18 which stop a planting part, etc. are comprised. On the left and right sides of the base, 16A of spare bristle holders for placing the spare caps for replenishing the bristle holders 16 in multiple stages are arranged.

As shown in FIG. 1 and FIG. 5, the fertilizer 7 is mounted on the self-propelled gas 3 between the driver's seat 15 and the planting device 4, and is separated from each other. (I) a fertilizer hopper 19 for saving fertilizer, a releasing mechanism 20 for releasing the fertilizer in the fertilizer hopper 19 by a set amount in conjunction with a planting operation, and a stop float 18 of the planting device 4. And a groove making machine 21 for forming a fertilizer groove in the paddy field as the gas is driven, and supplying the fertilizer transferred into the groove, and the fertilizer released through the hose 22. The electric fan 23, etc. which generate | occur | produce a gas for pumping in the air are provided and comprised.

As shown in FIG. 3, FIG. 4, the left side surface of the transmission case 9 has an lateral input shaft 49a interlocked with the output shaft 11a of the engine 11 via a belt transmission device 48. As shown in FIG. A hydrostatic stepless speed changer (HST) 49 as a peripheral speed gear having a gear is connected. The output of the hydrostatic stepless speed changer 49 is configured to be transmitted to the lateral axis in the transmission case 9. The input shaft 49a and the output shaft 49b of the hydrostatic stepless speed changer 49 are arranged back and forth.

The belt transmission device 48 spans the output pulley 48a mounted on the output shaft 11a of the engine 11 and the input pulley 48b mounted on the input shaft 49a of the hydrostatic stepless speed changer 49. The tension pulley 48d which winds the transmission belt 48c and gives tension to this transmission belt 48c is comprised.

The input shaft 49a of the hydrostatic stepless speed changer 49 extends to the right through the entire transmission case 9. The peripheral speed lever SL for operating this hydrostatic stepless speed change gear 49 is arranged on the left side of the steering wheel 14, and swings forward from the neutral of the peripheral speed lever SL. The forward speed can be changed, and the reverse speed can be changed by the swinging operation from the neutral to the rear.

In addition, a hydraulic pump 49c driven at the leading end of the input shaft 49a of the hydrostatic stepless speed change apparatus 49 is connected to the right side of the transmission case 9. On the upper surface of the transmission case 9, as shown in Figs. 3 and 4, a torque generator 14b constituting a hydraulic power steering device interlocked with the handle shaft 14a of the steering wheel 14, A control valve 6a of a work device lifting and lowering action for controlling the lifting cylinder 6 is attached.

The transmission case 9 is also used as a hydraulic oil tank. Specifically, the lubricating oil in the transmission case 9 is taken out as the working oil through the oil filter 9b attached to the right side of the transmission case 9, and is supplied to the hydrostatic stepless speed change apparatus 49 and the hydraulic pump 49c. Supplied. The pressure oil from the hydraulic pump 49c is supplied to the torque generator 14b, and is then supplied to the lifting cylinder 6 through the control valve 6a. Then, the drain oil of the hydrostatic stepless speed change apparatus 49 is returned to the front axle case 9a communicating with the transmission case 9, and the drain oil from the control valve 6a is directly transferred to the transmission case 9. It is supposed to return.

As shown in FIG. 12, FIG. 13, in the transmission case 9, the main clutch 50 which cuts off the output from the hydrostatic stepless speed transmission 49, and the output from this main clutch 50 are shown. The sub transmission 51 for shifting the gears into two stages and the differential mechanism 52 for transmitting the output from the sub transmission 51 to the left and right front wheels 1 are components of the traveling motor system. Array is installed. In the transmission case 9, further, between the one-way clutch 53 which transmits only the forward rotational power of the power branched from the driving motor system to the planting apparatus 4, and the stem which transmits power from the one-way clutch 53, The planting gear mechanism 54 for change and the planting clutch 55 which cuts off the power input from the planting gear mechanism 54 (cuts off the transmission of power to the planting device 4) diverge from the driving motor system. It is provided as a component of a motor system (planting motor system) to the used planting apparatus 4. That is, the main clutch 50 is provided as a clutch which cuts off the transmission to the running part and the planting apparatus 4, and is.

As the main clutch 50, a multi-plate friction type is adopted. In the input shaft 57, which is interlocked with the output shaft 49b of the hydrostatic stepless speed changer 49 via the spline coupling 56, the drive housing 58 is placed in the axial positioning in the axial direction. Is equipped. In the cylindrical clutch output shaft 59 mounted in the state in which the relative rotation is free in the input shaft 57 and in the axial center direction, the driven housing 60 is integrally rotatable and in the axial direction positioning. Is equipped. In this configuration, when the driven housing 60 moves in the axial center direction with respect to the drive housing 58 in accordance with the shifting of the clutch output shaft 59, between both (the driven housing 60 and the drive housing 58). The friction plates 61 mounted on the two sides are pressurized, and the two are interlocked. On the contrary, when the driven housing 60 moves away from the drive housing 58 in the axial direction, the interlock is released to the released state. do. The clutch output shaft 59 and the driven housing 60 are pressurized by the spring 62 in the interlocking state of the friction plate 61 (the direction in which the friction plates 61 are pressed). That is, it is comprised so that a clutch connection state may be shown by making the friction plate 61 an interlocking state, and a clutch disconnection state may be shown by making the friction plate 61 the release state.

As shown in FIG. 11 and FIG. 12, the main clutch 50 is operated only by the stepping operation of the gas stop pedal CBP provided at the right foot of the driving step S in the boarding operation unit 13. It is configured to be disconnectable. The gas stop pedal CBP is interlockedly connected to an upper surface of the transmission case 9 to a clutch operating shaft 63 which is pivotally mounted through a longitudinal axis P perpendicular to the input shaft 57. In addition, a pivot arm PSa is attached to the pedal shaft PS that is integrally rotated with the gas stop pedal CBP, and the pivot arm PSa and the clutch operating shaft 63 are provided on the outer projection of the transmission case. The east arm 63a is interlockedly connected by the interlocking rod RR. With such a configuration, the clutch operating shaft 63 is rotated to the normal region by the stepping operation and the stepping release operation of the gas stop pedal CBP.

At the distal end portion of the clutch operating shaft 63, a circumferential eccentric cam or shift operation cam 63b is formed by cutting a part of the periphery thereof. The shift operation cam 63b opposes the end face of the clutch output shaft 59. In the normal state in which the gas stop pedal CBP is not stepped on, as shown in FIG. 12, the shift operation cam 63b is rotated in one direction to release the pressure on the clutch output shaft 59. This results in the "connected" state of the main clutch 50. On the other hand, when the gas stop pedal CBP is pressed down, the shift operation cam 63b rotates in the opposite direction, so that the edge portion of the cam is displaced and pressed to the end face of the clutch output shaft 59, and pressurized by the spring 62. The clutch output shaft 59 moves in resistance. As a result, the driven housing 60 is displaced in the right direction in the figure, and the main clutch 50 is converted to the "cut off" state. In this clutch disconnection state, since the resistance is given to the rotation of the clutch output shaft 59 by friction between the edge portion of the shift operation cam 63b and the end face of the clutch output shaft 59, the clutch output shaft 59 The phenomenon of co-rotation (so-called co-rotation) with the input shaft 57 is prevented.

As the sub transmission 51, a gear shift type is adopted. The high speed large diameter transmission gear 65 and the low speed small diameter transmission gear 66 are integrally rotated together with the speed change input shaft 64 in the axial positioning direction. A shift gear 70 is mounted to the shift output shaft 67 so as to be integrally rotatable. The shift gear 70 has a high-speed position for engaging and engaging the small diameter gear portion 68 with the large diameter transmission gear 65, and the large diameter gear portion 69 with the small diameter transmission gear 66. It is possible to shift in the axial center direction at the low speed position to be interlocked and the neutral position not to be interlocked. The clutch output shaft 59 is provided with a small diameter output gear 71 which engages and engages with a large diameter transmission gear 65 to decelerate and transmit power, and is integrally rotatable to the clutch output shaft 59. 64) is decelerated interlocked. A sub transmission lever 180 for operating the sub transmission device 51 is disposed on the left side of the seat 15 (see FIG. 2).

The differential mechanism 52 is configured to be differentially lockable. That is, the shift member 74 is mounted on one side of the differential shaft 72 extending from side to side so as to be integrally rotatable and shiftable with the differential shaft 72, and as shown in FIG. The state where the member 74 separates from the differential case 73 becomes a normal differential lock release state. On the other hand, the shift member 74 is shifted to the right in the drawing to engage the end face of the differential case 73 so as to be in a differential lock state. The differential lock operation means for converting the differential mechanism 52 into the differential lock state and the differential lock release state is configured as follows. That is, the shift member 74 is pressed by the spring (not shown) to the differential lock release position, and at the same time, the differential lock pedal DP provided at the rear left side of the foot of the boarding drive unit 13 (Fig. 2). ) And the shift member 74 are interlocked, and in normal driving, the differential lock release state is maintained by separating the foot from the differential lock pedal DP. On the other hand, in the case of the entry and exit of the aircraft to the paddy field or the raising and lowering of the aircraft to the loading place of the transport vehicle, the differential lock pedal (DP) is operated by stepping on the heel of the left foot to bring the differential lock state to the left and right sides. The front wheel 1 can be driven at constant speed.

In the differential case 73 of the differential mechanism 52, an input gear 76 meshing with a shift output gear 75 splined to the shift output shaft 67, and a propeller shaft (equivalent to the main transmission shaft) (77) Is mounted to an output gear 79 that meshes with the gear 78 integrally formed therein. The propeller shaft 77 transmits the transmission power from the transmission case 9 to the rear wheel 2 via the rear axle case 10.

The one-way clutch 53 is provided so that only the forward rotation during the rotation of the speed change input shaft 64 is transmitted to the planting motor with the speed change input shaft 64 as a diverging point from the driving motor to the planting motor.

The planting mechanism 54 is configured as shown in FIG. That is, the cylindrical planting shift input shaft 82 is freely mounted on the shift output shaft 67 only at the same time, and is interlocked with the output gear 80 of the one-way clutch 53 via the gear 81. The planting gear input shaft 82 is mounted in a state in which a plurality of drive gears 83 having different diameters are rotated integrally. In addition, a group of driven gears 87, which are always engaged with and interlocked with each of the drive gears 83, interlocks with the planting gear output shaft 86 that interlocks with the planting clutch 55 via bevel gears 84 and 85. It is installed. Then, the electric ball 89 engages in the engagement recess 88 formed in the center hole of each driven gear 87, thereby linking the driven gear 87 to the planting transmission output shaft 86. Each electric ball 89 is mounted to the planting transmission output shaft 86 so as to be integrally rotatable, and the operation shaft 90 causes the electric ball 89 to be selectively engaged with the engaging recess 88. . That is, by selectively connecting the driven gear 87 to the planting transmission output shaft 86, the driven gear 87 used for transmission is changed to shift a plurality of stages (six steps in the example in the figure). It is configured to.

The front axle case 8 includes a differential shaft 72 and an electric shaft (not shown) for transmitting power therefrom to the front axle, and the rear axle case 10 includes a propeller from the transmission case 9. The power transmission mechanism for transmitting the power transmitted through the shaft 77 to the rear wheel 2 is built in.

As shown in FIGS. 11, 14, and 15, the rear axle case 10 is supported by the body frame 39 by a rolling freedom around a front and rear shaft center (corresponding to a rolling shaft center) X within a predetermined range. It consists of a lateral transmission case 93 and the longitudinal reduction case part 95 provided in succession to each of the left and right ends of this lateral transmission case 93. In the lateral transmission case 93, the lateral lateral direction in which power from the propeller shaft 77 extending backward from the transmission case 9 is distributed left and right through the bevel gear mechanism 91. Coaxial 92 is built in. In addition, each reduction case portion 95 is equipped with an axle 2A for supporting the rear wheel 2 and a reduction gear mechanism 94 for decelerating and interlocking the lateral transmission shaft 92 and the axle 2A. It is. The bevel gear mechanism 91 is composed of a drive side bevel gear 91A powered by a propeller shaft 77 and a driven side bevel gear 91B provided on the lateral transmission shaft 92. The driven side bevel gear 91B is provided on the side opposite to the friction type gas stop brake 99 with the propeller shaft 77 interposed therebetween. As a result, the collapse of the left and right weight balance of the lateral transmission case 93 is alleviated, and deterioration of the gas balance can be suppressed while arranging the brake 99 for stopping the gas to one side.

Electric transmission to each of the rear wheels 2 is particularly disconnected between the electric system to the rear wheels 2, specifically, between both ends of the lateral transmission shaft 92 and the respective reduction gear mechanism 94. A plate type side clutch or steering clutch 96 is provided therebetween. As shown in FIG. 14 and FIG. 15, each side clutch 96 is splined to the lateral transmission shaft 92 to integrally rotate with the lateral transmission shaft 92 and at the same time, the lateral transmission shaft. A boss member (corresponding to the driving side boss member) 96A capable of shifting operation in the axial direction of 92 is provided, and a driven side drum 96B interlocked with the reduction gear mechanism 94. The plurality of friction plates 96C are distributed and mounted as a drive side friction plate 96Ca externally supported by the boss member 96A and a driven side friction plate 96Cb which is fitted to the inner circumference of the driven side drum 96B. . Then, as the boss member 96A is shifted to the outside of the body, the driving side friction plate 96Ca is pressed against the driven side friction plate 96Cb, and both friction plates are frictionally interlocked (the clutch is brought into a connected state). On the contrary, as the boss member 96A is shifted inward to the body side, the driving side friction plate 96Ca is pressed against the driven side friction plate 96Cb, and the friction interlocking of both friction plates is released (the clutch is in a shut-off state). being). In each side clutch 96, a clutch spring 96D for pressing and pushing the boss member 96A to the clutch connection side is externally fitted to the lateral transmission shaft 92. As shown in FIG.

The reduction gear mechanism 94 is arranged on the side outside of the driven drum 96B of the side clutch 96, and has a small diameter first gear G1 which rotates integrally with the driven drum 96B. Large diameter second gear G2, small diameter wide third gear G3 coaxially rotating with the second gear G2, and axle 2A of the rear wheel 2, which are fitted in the same direction. The 4th gear G4 of large diameter connected to the structure is comprised so that deceleration of two steps may be performed. Here, by arranging the gear pairs consisting of the third gear G3 and the fourth gear G4 inside the body and placing them under the side clutch 96, the reduction case 95 becomes wider in the lateral outward direction. Is suppressed.

As shown in FIG. 14, a gas stop brake 99 is provided between the deceleration case portion 95 on the right side and the boss member 96A. The gas stop brake 99 is rotated by engaging a friction plate (corresponding to the friction plate on the rotating side) 99a and a deceleration case portion 95 that are externally mounted with a spline on the outer circumference of the boss member 96A. By pressing the stationary friction plate (corresponding to the friction plate on the fixed side) 99b, the boss member 96A and the lateral transmission shaft 92 which rotates integrally therewith are configured to be braked. And since the cup-shaped operation member 98 loosely fitted to the boss member 96A is moved to the outer side (right direction in FIG. 14) next to a base body, the friction plates 99a and 99b are pressed against each other.

The gas stop brake 99 is operated by the brake operation shaft 100 mounted on the upper surface of the reduction case part 95 around the longitudinal axis P1 by a rotational free passage. Specifically, the shift fork 101 is mounted on the indentation portion of the brake operating shaft 100, and the shift fork 101 is arranged to face the end face of the operating member 98. By rotating the shaft 100, the operation member 98 is shifted through the shift fork 101, and the boss member 96A can be braked.

An operation arm 100a is provided on the case outer protrusion of the brake operation shaft 100. As shown in FIG. 11, this operation arm 100a is interlockedly connected to the said main clutch brake pedal (gas stop pedal) CBP via an interlocking rod (an example of a brake interlocking rod) 110, According to the stepping operation of the gas stop pedal CBP, the linkage rod 110 is tension-displaced forward, and the gas stop brake 99 is braked. On the other hand, when the gas stop pedal CBP is released and returned to its original position, the braking of the gas stop brake 99 is released. Here, since the gas stop pedal CBP is also connected to the main clutch 50 via the pedal shaft PS as described above, the gas stop pedal CBP functions as the main clutch brake pedal. The main clutch 50 is first shut off by the stepping operation of the gas stop pedal CBP, and the braking is applied by the stepping operation.

In addition, the linkage rod 110 is provided with a turnbuckle (110a), by adjusting the expansion and contraction with the turnbuckle (110a), it is possible to adjust the operation timing of the gas stop brake 99 to the main clutch (50). .

The operation structure of the left and right side clutches 96 is configured as follows. As shown in FIGS. 14 and 15, the clutch operating sleeve 102 is slidably loosely fitted to the lateral transmission shaft 92, and the thrust collar 103 is formed on the end face of the boss member 96A. Are face to face through. On the upper surface of the reduction case portion 95, a clutch operating shaft 104 is pivotally mounted around the longitudinal axis P2. An eccentric cam 105 is formed at the indentation end portion of the clutch operation shaft 104 and is disposed opposite to the end face of the clutch operation sleeve 102. As a result, the side clutch 96 is configured to be disconnected by the rotation operation of the clutch operation shaft 104.

The left and right side clutches 96 are configured so that only the inner side of the swing is automatically turned off based on the gas steering operation. For this reason, the steering clutch operating mechanism Z which reversibly cuts | disconnects the steering clutch 96 of a turning inside according to steering operation more than a set angle from the straight state of the front wheel 1 as an operation mechanism of the steering clutch 96 is therefore. Is installing.

Specifically, as shown in FIGS. 11 and 14, the pitman arm 111 is swung left and right so as to steer the front wheel 1 to the left and right of the knuckle arm 118 of each of the front wheels 1. It is linked with the drag link (119). The pitman arm 111 is connected to the relay link 113 through a rod 112 that is pushed and pulled so as to swing around the longitudinal axis Y in accordance with the steering operation (left and right swing) of the pitman arm 111. have. The link 114 to be distributed is interlocked with the relay link 113, and the distribution link 114 is configured to swing in one direction of the relay link 113 when the pitman arm 111 is steered to the left. Thus, by swinging in the one direction around the longitudinal axis Y, the clutch operating shaft 104 on the left side is pulled and rotated from the clutch connection phase to the clutch interruption phase via the rod 116 (an example of the clutch linkage rod). On the contrary, when the pitman arm 111 is steered to the right, the clutch operating shaft 104 on the right side is swung in the opposite direction around the longitudinal axis Y in accordance with the swing in the opposite direction of the relay link 113. Is rotated via the rod 116 from the clutch connection phase to the clutch interruption phase.

A pin pivot support connecting hole 115 with a rod 112 that is pushed and pulled is formed in the operation tool 111a provided in succession to the pitman arm 111. The hole 115 is formed as a long hole, and the length is a rod that pushes and pulls the swing of the pitman arm 111 only when the pitman arm 111 swings at a set angle (eg, 30 °) or more from a straight posture. It is transmitted to (112), and fluctuations below the set angle are set not to be transmitted. In addition, a long hole 117 is formed at the connection portion between the distribution link 114 and the rods 116 on the left and right sides, respectively. The length of each long hole 117 is set so that the operation force does not act on the other rod 116 in the state in which the rod 116 of the turning inner side is pulled and operated so that only the side clutch 96 of the turning inner side may be blocked. It is.

By constructing the steering clutch operating mechanism Z as described above, if the left and right front wheels 1 are steered larger than the set angle to turn the aircraft largely, the swing of the pitman arm 111 is transmitted through the relay link 113. Only one side clutch 96 which is transmitted to the distribution link 114 and connected to the rod 116 to be pulled forward is blocked. That is, only the side clutch 96 on the inside of the swing is cut off, and the body turns by the "three-wheel drive" of the front wheel on the left and right and the rear wheel 2 on the outside of the swing. At this time, since the rear wheel 2 inside the swing in a loose rotation state follows the ground in accordance with the swinging movement of the gas, the rear wheel 2 rotates without causing the rice paddy to unreasonably ruin the paddy field.

Next, the drive structure of the release mechanism 20 of the fertilizing device 7 will be described. Referring to FIG. 9, a drive case 24 for driving the release mechanism 20 is provided at a portion of the propeller shaft 77 approaching the rear axle case 10. In this drive case 24, there is housed a transmission mechanism 25 for taking out branching power from the propeller shaft 77 to the release mechanism 20. The transmission mechanism 25 attaches and fixes the output bevel gear 27 to the propeller shaft 77 via the one-way clutch 26, and at the same time perpendicular to the axis of the propeller shaft 77, the output shaft 28 ) Is arranged.

The drive case 24 consists of the main body case part 24A which is attached and supported by the propeller shaft 77 via the bearing 29, and the output case part 24B which covers the output shaft 28. As shown in FIG. In the output case 24B, the bevel gear 30 meshing with the output bevel gear 27 is supported through the bearing 31, and the output end of the output shaft 28 is also supported. The input end of the output shaft 28 is internally fitted and supported in the bevel gear 30 in a loose rotation state.

Furthermore, the fertilizing clutch 32 is provided in the output case part 24B. The fertilizing clutch 32 externally fits the clutch sleeve 33 so as to be movable in the axial center direction to the output shaft 28, and simultaneously faces the surfaces of the clutch sleeve 33 and the output bevel gear 30 to each other. A clutch click is formed respectively, and the opposing clicks are engaged with each other so that power transmission is possible, and the power transmission is interrupted by being separated from each other.

As shown in Fig. 5, the output shaft 28 protrudes from the output case portion 24B, and a rotation driving arm 34 is attached to the protruding end. The rotary drive arm 34 and the driven arm 35 attached to the rotary shaft of the release mechanism 20 are interlocked with each other by the connecting rod 36, so that the release mechanism 20 is driven.

Next, the input unit structure in the rear axle case 10 will be described. Referring to Fig. 6, the input shaft 37 to which the driving side bevel gear 91A of the bevel gear mechanism 91 is attached is disposed on the same axis as the propeller shaft 77, and is provided at the tip of the input shaft 37. The concave connection portion 38 is formed inwardly of the shaft. This connecting part 38 is provided by forming a spline in the recessed inner peripheral surface. A spline is also formed at the tip of the propeller shaft 77, and the spline is fitted to the spline on the side of the connecting portion 38 of the input shaft 37, thereby enabling power transmission. Thus, the concave construction of the connecting portion of the input shaft 37 is a coupling 106 necessary for projecting the input shaft 37 from the rear axle case 10 and interlocking with the propeller shaft 77 at the protruding end thereof. ), The drive case 24 and the rear axle case 10 can be installed close to each other.

Next, the rolling structure of the rear axle case 10 will be described.

As shown in FIG. 6 and FIG. 8, frame brackets 39A are provided at the rear ends of the left and right pairs and the front and rear gas frames 39 and 39, respectively. In addition, support brackets 40 and 41 for supporting the rear axle case 10 by a rolling free path are arranged before and after the rear axle case 10. The front support bracket 40 externally fits the center boss portion 40A to the front boss portion 10A of the rear axle case 10 and the rear axle case 10 is the shaft center of the front boss portion 10A. Support freely around. On the other hand, the rear support bracket 41 inserts and fits the shaft 41A provided in the center part in the candidate part 10B of the rear axle case 10, and the rear axle case 10 is inserted into the candidate part 10B. Support freely around the center of the shaft.

As described above, the rear axle case 10 is supported by the front and rear support brackets 40 and 41, and becomes a rolling free operation centering on the axes of the front boss part 10A and the candidate part 10B. Here, the battery bracket 40 and the backing bracket 41 are referred to as point brackets.

In the support bracket 40 on the front side, the attachment sheets 40B and 40B extending left and right are attached to the lower surfaces of the gas frames 39 and 39, and in the support bracket 41 on the rear side, the attachment sheets 40 extend in the left and right sides. 41B and 41B are attached to the lower surfaces of the frame brackets 39A and 39A, and the rear axle case 10 is supported.

As shown in FIG. 6 and FIG. 7, the brackets are successively installed from the rear axle case 10 toward the upper portion 41C of the support bracket 41, and receive the neutral return spring 43 for rolling. The inside is comprised by the spring receiving part 42. As shown in FIG. As shown in FIG. 11, the spring receiving parts 42 and 42 are provided to the left and right, and both are extended toward 41C of the up-right upright part of the rear support bracket 41. As shown in FIG. As shown in FIG. 7, the bolt 44 penetrates through 42A of through-holes formed in the spring receiving part 42, and the nut 45 is screwed in the downward end part of this bolt 44, and the nut ( A spacer 46 is interposed between 45 and the head of the bolt 44, and a pressure plate 47 is provided between the spacer 46 and the head of the bolt 44. The neutral return spring 43 is fitted into the pressing plate 47 and the spring receiving portion 42 to fix the neutral return spring 43. The initial setting length of the neutral return spring 43 can be set by adjusting the tightening amount of the nut 45.

The pressing plate 47 is in contact with the lower surface of the frame bracket 39A, and when the rear axle case 10 is rolled, the neutral return spring 43 on either side is pressed and contracted, and the bolt 44, The nut 45, the spacer 46, and the pressing plate 47 are integrally moved downward with respect to the spring receiving part 42, and the installation length of the neutral return spring 43 becomes short, and the neutral return Power.

In addition, as shown in FIG. 16, the said bolt 44 may be comprised by the end mounting bolt. In this case, since the fastening position of the nut 45 is determined at the end 44A, the initial length of the neutral return spring 43 is set, but the spacer 46 shown in the figure can be omitted.

As shown in FIG. 6, FIG. 7, and FIG. 11, the spring receiving part 42 extended toward the back from the rear axle case 10 extends toward 41 C of upright parts of the support bracket 41 of the rear side. It is provided near the part 41C which stood out, and the tip part which extended and extended. As a result, even when the rear axle case 10 yaws, the left and right spring bearing portions 42 abut against the upright portion 41C, thereby preventing the yawing operation. Here, the spring receiving part 42 and the backing bracket 41 are called yaw blocking mechanisms A of the rear axle case 10.

(Other Embodiments)

As mentioned above, although the riding type power receiver which concerns on this invention was described as an example by the rice transplanter which is the representative example, the preferable embodiment is not limited to the said Example.

For example, in the above embodiment, as the yawing stop mechanism A of the rear axle case 10, a configuration using the spring receiving portion 42 of the neutral return spring 43 is shown. The rear axle case 10 From the spring receiving part 42, the exclusive contact part may be extended, and the contact part may contact the part 41C which has been raised above the rear support bracket 41, thereby preventing the yawing operation.

In addition, as shown in FIG. 17, the recessed part Ha is formed in the right side surface of the rear bonnet HR which covers the rear part of the engine 11, and it arranges in the upper vicinity of the front axle case 8 from the side view. The gas stop pedal (main clutch brake pedal) CBP that is used may be arranged in a state in which the recessed portion 97a is placed. Thereby, compared with the case where there is no recessed part 97a, the space for the step of the boarding driver 13 can be formed without difficulty, and the habitability in the boarding unit 13 can be improved. . In addition, when ascending and descending in the operation step S, the ascending and descending from the front of the gas also becomes easy even in the right side part SR where the gas stopping pedal CBP is arranged.

According to the present invention, since the gas rotates by driving by the left and right front wheels and the rear wheels on the outside of the revolution, the rear wheels on the inside of the revolution loosely rotate at this time.

In addition, when the vehicle stop pedal is pressed while driving without blocking the side clutch, the lateral transmission shaft, which is the transmission shaft connected to the traveling system, is braked, thereby braking not only the rear wheel but also the front wheel. The gas can be stopped. In addition, if the steering wheel is operated while the front wheel is steered and the side clutch is shut off and the vehicle is turned down, the aircraft can be stopped by applying braking to the three wheels except for the rear wheel inside the swing.

In forming the brake for gas stop, the boss member constituting one side clutch is also used as the support member of the friction plate constituting the friction brake.

Therefore, by turning the front wheels and turning only the side clutch on the inside of the swing, the problem is found in the conventional configuration of turning using side clutches and brakes. It is possible to suppress phenomena such as increasing the running load or increasing the running load, and to enable smooth gas swinging lightly.

In addition, since the friction plate on the rotating side of the brake is supported by the boss member supporting the driving side friction plate constituting the side clutch, a structure for braking the lateral transmission shaft in the rear axle case can be obtained while the parts are used interchangeably. It is possible to increase driving and turning performance while simplifying the structure.

According to the present invention, since the gas stop brake is provided only on the boss members of the left and right side clutches, the weight of the side on which the gas stop brake is provided in the gas left and right directions is increased. However, since there is a driven bevel gear on the opposite side of the brake, the collapse of the left and right weight balance of the rear mounting shaft case is alleviated.

Therefore, deterioration of the gas balance can be suppressed while the stop brakes are arranged side by side.

In the present invention, the yawing operation of the rear wheel case is prevented by the yaw blocking mechanism. In particular, since this blocking mechanism is provided near the rolling shaft center, there is little need to improve the strength of the rolling support structure against the yawing motion.

Therefore, as a rolling support structure, it is good only to maintain the structure which can ensure a rolling function, and it is advantageous in terms of manufacturing cost.

The rear axle case is freely supported by the branch brackets, and spring bearings receiving the neutral return springs for rolling are respectively provided on both sides of the rolling shaft core, and the yawing mechanism is connected to the spring bearings and the branch brackets. When it is configured to prevent the yaw motion of the rear axle case by contacting with the spring, the spring support provided in contact with the point bracket can be used as the yaw stop mechanism of the rear axle case, thereby reducing the number of parts and It is further advantageous because the structure can be simplified.

Claims (5)

As a riding type faucet working machine configured to transmit the shifted power to the front and rear wheels 1, which are free to steer, and the rear and rear wheels 2, which cannot be steered, The left and right rear wheels are provided with a pair of left and right frictional side clutches 96 for inserting and breaking power transmission for each rear wheel, and these rear wheels are axially supported by the rear axle case 10. The body which is configured to cut off the side clutch 96 located inside the swing by steering operation of the left and right front wheels 1 by the steering wheel 14 and is operated by the operation of the gas stop pedal CBP. In the passenger type power receiving machine equipped with the stop brake 99, The rear axle case 10 is composed of a lateral transmission case 93 and a longitudinal reduction case portion 95 connected to the left and right ends of the lateral transmission case, respectively. While the side clutch 96 is installed in the deceleration case part 95, the gas stop brake 99 is installed in the deceleration case part 95, A clutch linkage rod 116 for operating the respective side clutches 96 and a brake linkage rod 110 for operating the gas stop brake 99 extend to the rear axle case 10, and The clutch operation shaft 104 operated by the clutch linkage rod 116 and the brake operation shaft 100 operated by the brake linkage rod 110 protrude in the one reduction gear case 95. A riding type faucet working machine, characterized in that. The shift fork 101 for operating the gas stop brake 99 is provided at the inrush portion of the brake operating shaft 100 into the rear axle case 10. Riding faucets. 3. The shift fork according to claim 2, wherein the shift fork 101 is arranged to face the end face of the operation member 98 for operating the gas stop brake 99. A riding type, characterized in that the gas stop brake (99) is configured to be braked as the operating member (98) is shifted through the shift fork (101) while rotating the brake operating shaft (100). Faucets. An eccentric cam (105) for manipulating the side clutch (96) is provided in a rush portion of the clutch operating shaft (104) into the rear axle case (10). Type faucets. The said side clutch operation shaft 104 is penetrated by the upper surface of the said one speed reduction case part 95, and the lower end part is the said speed reduction case part 95 in any one of Claims 1-4. A passenger-type faucet working machine, which is supported by a support hole formed below.