JP2000009163A - Paddy field working machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To stop a machine body only by the operation of a main clutch by providing a braking means for imparting braking action to a travel transmission system on the transmission lower side of a main clutch interlockingly with main clutch off operation. SOLUTION: A ring-like brake member 43 whirl-stopped being engaged with an engaging part 42 is rotatably fitted with play between a gear G2 meshed with a gear G1, and a ring member 41. The ring member 41 is pressed and displaced onto the gear G2 side through a bearing 44 when a clutch drum 31 is shifted in the clutch off direction. In the off state of a main clutch, the ring member 41 is shifted by shifting the clutch drum 31 onto the gear G2 side, which results in holding a brake member 43 between the gear G2 and the ring member 41, and braking action is imparted to the ring member 41 and the gear G2 which is a driven side rotating member, by friction with the nonrotatable brake member 43 to brake a transmission system on the transmission lower side of the main clutch C.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a paddy field working machine such as a rice transplanter or a submerged direct sowing machine.

[0002]

2. Description of the Related Art In a riding type rice transplanter which is a typical paddy field working machine, a main clutch is operated by a pedal, and side brakes provided on right and left rear wheels are independently operated by a brake pedal. When traveling, connect the left and right brake pedals so that the left and right side brakes can be operated at the same time, and in the field, operate the left and right brake pedals independently to make small turns such as at the ridge. I have.

[0003]

In the above-mentioned conventional construction, in order to stop the aircraft when traveling on a slope such as a slope at an entrance to a field, the main clutch is disengaged and the connected left and right brake pedals are operated. To operate both side brakes at the same time, but if the brake pedal is depressed later than the main clutch disengagement operation, the aircraft may slip down the slope, which is not sufficient for operation. Attention was needed. Further, when a multi-plate friction clutch is used as the main clutch, even when the clutch is disengaged, a slight power is transmitted to the traveling power transmission system due to the entrainment phenomenon, and the aircraft may slightly move. I needed to handle it.

The present invention has been made in view of such a point, and has as its main object to improve the handleability by enabling the machine to be stopped only by operating the main clutch.

[0005]

Means for Solving the Problems [Structure, operation and effect of the invention according to claim 1]

(Structure) The invention according to claim 1 is a paddy field work in which the engine power is driven via a main clutch to drive the left and right front wheels and rear wheels, and the left and right rear wheels are provided with side brakes respectively. The machine is characterized in that it is provided with a brake means for applying a braking action to a traveling transmission system on the lower transmission side of the main clutch in conjunction with the disengagement operation of the main clutch.

(Operation) According to the above configuration, the left and right side brakes are operated to stop the traveling body, and only one of the side brakes is operated to make a small turn, so that the rear wheel brake is operated. Makes a turn.
Further, if the main clutch is disengaged while traveling on a slope, the traveling transmission system is braked in conjunction therewith, and the body does not slip down.

(Effects) Therefore, according to the first aspect of the present invention, when the aircraft is stopped while traveling on an incline, the main clutch can be operated without worrying about a delay in brake operation, and handling is improved. Can be improved.

[Structure, operation and effect of the invention according to claim 2]

(Structure) According to a second aspect of the present invention, in the first aspect, the left and right front wheels are driven via a differential device, and the left and right rear wheels are driven via a side clutch and the side brake. With this configuration, the side brake is operated to be braked by an operation subsequent to the disengagement operation of the side clutch.

(Operation) According to the above configuration, the right and left rear wheels, which are the main propulsion wheels, are driven at the same speed via the side clutch during the work traveling in the field, and the inside of the turning is turned when the body turns on the ridge. By turning off only the side clutch of the rear wheel that is to be turned, it is possible to perform a gentle turning by one drive, and by disengaging the side clutch of the rear wheel inside the turning and braking the side brake, A small turning can be performed. Further, when the vehicle is traveling on a slope, the vehicle can be stopped by braking the traveling power transmission system simply by disengaging the main clutch.

(Effects) Therefore, according to the second aspect of the present invention, it is possible to perform work traveling with excellent straightness in a field, and to perform a smooth small turn with few headlands on a ridge. And, when traveling on slopes, the aircraft can be easily and easily stopped without slippage,
Operability and handleability are high.

[Structure, operation and effect of the invention according to claim 3]

(Structure) According to a third aspect of the present invention, in the first aspect of the present invention, the main clutch is constituted by a multi-plate clutch, and the brake means is operated by moving an operating member of the main clutch to a clutch disengagement side. In conjunction with the operation, the non-rotatable brake member is sandwiched between a pair of driven rotation members.

(Operation) According to the above configuration, when the main clutch is disengaged, the operating member of the main clutch is moved to the clutch disengaged side, and in conjunction with this, the brake member is sandwiched between the pair of driven side rotating members. On the other hand, the driven-side rotating member whose power transmission is interrupted is braked by a frictional action with the brake member. When the main clutch is engaged, the gripping of the brake member by the rotating member on the driven side is released, and the friction braking is released.

(Effect) Therefore, according to the third aspect of the present invention, since a single brake member is sandwiched between a pair of driven side rotating members to apply friction braking, a large friction braking area can be secured and reliable. Braking can be performed.

[Structure, operation and effect of the invention according to claim 4]

(Structure) According to a fourth aspect of the present invention, in the first aspect of the present invention, the main clutch is constituted by a multi-plate clutch, and the brake means includes a clutch fork for operating the main clutch, and a clutch disengagement side. The clutch fork moved to is constituted by a rotating member on the driven side that is indirectly or directly contacted and pressed, and in a state where the main clutch is disengaged,
The clutch fork is configured to apply frictional braking to the driven rotary member.

(Operation) According to the above configuration, when the main clutch is disengaged, the clutch fork moved to the clutch disengagement side is indirectly or directly pressed against the rotating member on the driven side. At this time, since the clutch fork is non-rotatably engaged with the main clutch, the clutch fork itself functions as a non-rotatable brake member, and the driven rotary member is frictionally braked.

(Effects) Therefore, according to the invention of claim 4, it is possible to constitute a brake means for applying frictional braking without preparing a dedicated non-rotatable brake member, thereby simplifying the structure. Function can be obtained during

[Structure, operation and effect of the invention according to claim 5]

(Structure) According to a fifth aspect of the present invention, in the first aspect of the present invention, there is provided a clutch disengagement locking means for fixing the main clutch in a disengaged state.

(Operation) According to the above configuration, the main clutch in the clutch disengaged state is fixed by the clutch disengagement locking means, so that the braking state can be maintained as it is, so that the parking can be performed without another parking brake operation. A braking state is obtained.

(Effects) Therefore, according to the fifth aspect of the present invention, the above-mentioned effects of the invention according to any one of the first to fourth aspects are provided, and the aircraft is parked simply and safely. And practical convenience is high.

[0025]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows a riding rice transplanter as an example of a paddy working machine to which the present invention is applied. In this rice transplanter, a four-row seedling planting device 5 is connected to a rear part of a four-wheel drive type traveling body 3 having a front wheel 1 and a rear wheel 2 via a hydraulically driven link mechanism 4 so as to be able to move up and down. It is configured. An engine 6 is mounted on a front portion of the traveling body 3, and the engine output is transmitted to a transmission case 7 that supports the front wheels 1 via a belt transmission 8, and the transmission gears are further shifted by the transmission case 7 so that the front wheels 1 are moved. While being driven, the speed change output taken out of the transmission case 7 is shaft-transmitted to a rear transmission case 9 that supports the rear wheel 2, and the working power taken out of the rear part of the transmission case 7 is used for planting the seedlings. The shaft is transmitted to the device 5.

FIG. 2 shows the transmission structure of the rice transplanter. The output of the engine 6 is input to a first shaft 11 of the transmission case 7 via a belt transmission 8 and is transmitted to a gear G1 via a multi-plate clutch type main clutch C mounted on the first shaft 11. The power of the gear G1 is transmitted to the second transmission shaft 12 via the gear G2. Between the second transmission shaft 12 and the third transmission shaft 13, two forward stages, one reverse stage
There is provided a traveling gear transmission mechanism 14 for performing a speed change, and this gear transmission mechanism 14 causes a forward low speed as a “planting speed”, a high forward speed as a “moving speed”, and
"Reverse" is selected by operating the shift gear SG. The power of the third transmission shaft 13 is transmitted to the left and right differential shafts 16 via the differential mechanism 15, and the power of the differential shaft 16 is transmitted to the left and right front wheels 1. Further, rear wheel driving power is taken out from the differential mechanism 15 toward the rear of the fuselage via a transmission shaft 17.

The power of the second transmission shaft 12 is taken out to the PTO shaft 21 via the inter-stock transmission mechanism 18, the torque limiter 19, and the planting clutch 20, and is transmitted to the seedling planting device 5 by shaft. . As shown in FIG. 3, the left and right differential shafts 16 of the differential mechanism 15 can be integrated as needed by a differential lock mechanism 22 so that the left and right front wheels 1 can be driven at a constant speed. A part of the output of the engine 6 drives a hydraulic pump P, which is a drive source for raising and lowering the link mechanism 4.

Rear transmission case 9 supporting left and right rear wheels 2
Are rotatably mounted, and the power from the transmission shaft 17 is transmitted to the left and right rear wheels 2 via the left and right side clutches 25 and the side brakes 26. The side clutch 25 and the side brake 26 are configured such that the side clutch 25 is firstly disengaged in the first shift of the shift member 27, and the side brake 26 is braked in the subsequent second shift of the shift member 27. The left and right shift members 27 are linked to a pair of left and right brake pedals 29 provided on the right side of the operation step 28.

As shown in FIGS. 3 and 4, the main clutch C is provided between a clutch drum 31 spline-fitted to the first transmission shaft 11 and a spline boss 32 loosely fitted to the first transmission shaft 11. The friction plate 33 engaged with the clutch drum 31 and the friction plate 34 engaged with the spline boss 32
As shown in FIG. 4, the clutch plates 31 are urged to slide to the right in the drawing by a built-in disc spring 35 so that the friction plates 33 and 34 are grouped. Is pressed to transmit power from the clutch drum 31 to the spline boss 32 (with the clutch in).
As shown in FIG. 5, the clutch drum 31 is slid to the left in the drawing against the disc spring 35 to release the pressure contact of the friction plates 33 and 34, so that the clutch drum 31 is moved from the clutch drum 31 to the spline boss 32. Power transmission is interrupted (clutch disengaged).

The clutch case 36 for sliding the clutch drum 31 is mounted on the transmission case 7.
A cam member 38 fixedly connected to the clutch operating shaft 37 with a pin and a boss portion 36 of the clutch fork 36 are slidably fitted on the clutch operating shaft 37 inserted and supported by the clutch fork 36.
A climbing cam portion 39 is formed between the cam portion 39 and a.
The outer end of the clutch operating shaft 18 and the main clutch pedal 40 provided on the left side of the operation step 28 in the traveling machine body 3 are linked and linked, and the main clutch pedal 4
When the clutch operation shaft 37 is rotated by depressing 0,
As shown in FIG. 5, the cam member 3 cannot rotate with respect to the clutch fork 36 which cannot rotate due to engagement with the clutch drum 31.
When the fork 8 is forcibly rotated, the clutch fork 36 is relatively slid leftward in the drawing by the cam action of the climbing cam portion 39 to bring the clutch disengaged state.

The main clutch C is equipped with a brake mechanism B having the following structure. That is, the gear G1 is integrally formed at one end of a spline boss 32 which is a driven member of the main clutch C, and the ring member 41 is externally engaged with the gear G1 and the gear G2 engaged with the gear G1. A ring-shaped brake member 43, which is engaged with an engagement portion 42 formed on the inner wall surface of the transmission case 7 and is prevented from rotating, is freely rotatably fitted between the and the ring member 41. A bearing 44 is interposed between the ring member 41 and the clutch drum 31 so that the clutch drum 31 is disengaged in the clutch disengaging direction (left direction in the drawing).
Is shifted to the bearing 44
And is pushed and displaced toward the gear G2.

According to the brake mechanism B having the above structure, FIG.
5, the brake member 43 is in a free state between the gear G2 and the ring member 41. However, in the main clutch disengaged state shown in FIG.
Is shifted to the gear G2 side so that the ring member 4
1 is shifted so that the brake member 43 is sandwiched between the gear G2 and the ring member 41, and the friction with the non-rotatable brake member 43 causes the gear G2 and the ring member 41 which are the driven rotary members to rotate. , And the transmission system on the lower transmission side of the main clutch C is braked.

Some of the other embodiments of the present invention are exemplified below.

[First Example] As shown in FIGS. 6 and 7,
An interlocking shaft 52 linked via a link 51 to a main clutch pedal 40 for operating a main clutch C having no brake mechanism B is laid horizontally, and the right end of the interlocking shaft 52 and the left and right brake pedals 29 are long. When the clutch is disengaged by depressing the main clutch pedal 40, the two brake pedals 2 are linked via the link 51, the interlocking shaft 52, and the link 54.
9 are operated to the stepping side, and the shift members 27 for the respective rear wheel transmission systems are both operated to the side brake operating position. According to this configuration, the transmission to the left and right rear wheels 2 is cut off in conjunction with the disengagement operation of the main clutch C, and braking is applied to each of the main body C and the traveling body 1
Stops.

A manual operation lever 55 is connected to the main clutch pedal 40 so that the vehicle 1 can be moved down on the ground to operate the traveling machine 1 in order to cross over a ridge or to load or unload a truck. The main clutch C can be turned off by hand, and the traveling machine body 1 can be braked with the turning operation.

As shown in FIG. 8, a clutch release lock lever 56 for locking and fixing the main clutch pedal 40 at the depressed position is provided on the step 28.
The main clutch C is disengaged so that the state in which the vehicle body braking is applied can be maintained.

[Second Example] FIGS. 9 to 12 show a transmission case 7 in a model in which five or more rows are planted.
A part of the internal structure of is shown. In this example,
The engine output is input to a first transmission shaft 61 via a belt-type continuously variable transmission mechanism (not shown), and then transmitted to a second transmission shaft 62 via a gear G3 and a gear G4. It is transmitted to gears G5 and G6 via C. The power of the gears G5 and G6 is transmitted to a third transmission shaft 64 via a constant mesh type forward / reverse switching mechanism 63, and further transmitted to a fourth transmission via a gear transmission mechanism 66 which performs three-speed shifting by a shift gear 65. It is transmitted to the shaft 67 and the differential mechanism 68, and the differential shafts 69 and 69 of the differential mechanism 68 are transmitted.
The left and right front wheels 1 and 1 are driven via the transmission shaft 70 and the power branched from the differential mechanism 68 is transmitted to the rear transmission case 9 at the rear of the fuselage.
Are driven via a side clutch and a side brake, respectively. The differential mechanism 68 is equipped with a differential lock mechanism 71, which can drive the left and right front wheels 1, 1 at a constant speed as needed. Although not shown, the second transmission shaft 6
4 is taken out from the gear G7, and only the forward rotation power is supplied to the one-way clutch, the inter-gear transmission mechanism,
In addition, the shaft is transmitted to the seedling planting device 5 via a planting clutch.

FIG. 10 shows the main clutch C and the forward / reverse switching mechanism 63. The main clutch C
Are the gears G5 and G loosely supported by the second transmission shaft 62.
6 and a clutch drum 72 integrated with the second transmission shaft 62.
Boss 73 fitted with spline so that it can be shifted to
Between the friction plate 74 engaged with the clutch drum 72
And friction plates 75 engaged with the spline bosses 73 are alternately laminated, and the spline bosses 73 are slid to the left in the figure by the coil springs 76 as shown in FIG. By pressing the friction plate 7
The power transmission from the spline boss 73 to the clutch drum 72 and the gears G5 and G6 is performed by pressing the groups 4 and 75 (clutch engagement), and the spline boss 73 is opposed to the coil spring 76 as shown in FIG. By sliding the group of friction plates 74 and 75 to the middle and right to release the pressure contact, the clutch drum 72 and the gear G
5. Power transmission to G6 is cut off (clutch disengaged).

The main clutch C constructed as described above can be freely turned on and off by the main clutch pedal 40, and can be automatically turned on and off by switching between forward and backward. That is, a bearing 77 is externally mounted on the end of the spline boss 73 that controls the on / off of the main clutch C, and a hydraulic cylinder 78 is provided on the outside in the axial center direction. A ring-shaped piston 79 facing the inner ring 77a of the bearing 77 is fitted in the hydraulic cylinder 78, and the piston 79 is moved to the right in the drawing by supplying hydraulic oil into the cylinder, so that the bearing 79 By pressing the spline boss 73 through the inner ring 77a of the motor 77 to bring the clutch into a disengaged state, oil pressure is released from the hydraulic cylinder 78 to release the pressing of the spline boss 73, and the clutch is engaged by the urging force of the coil spring 76. It is configured to bring.

A shift fork 82 for operating a shift boss 81 of the forward / reverse switching mechanism 63 is connected to an operation shaft 83 which is inserted through the transmission case 7 in a transverse direction. The forward / backward switching lever 8 is linked via a link mechanism 85 to a forward / backward switching lever 84 provided in the section.
When the front lever 4 is pivoted forward or backward, the operation shaft 83 is slid left and right, and the shift fork 82 selectively engages the shift boss with the forward gear G8 or the reverse gear G9. The other end 83a of the operation shaft 83 is connected to a control valve 86 for the hydraulic cylinder 78.
Operating shaft 83 is in the forward position F
Alternatively, when in the reverse position R, the hydraulic cylinder 78 communicates with the transmission case 7 via the in-shaft oil passage 87 of the second transmission shaft 62 and the in-shaft oil passage 88 of the operation shaft 83, and When drainage is permitted and the main clutch C is engaged and the operating shaft 83 is displaced from the forward position F and the reverse position R, the pressure oil from the pump P is supplied to the in-shaft oil passage 87.
Is supplied to the hydraulic cylinder 78 and the main clutch C is brought into the disengaged state, so that forward / reverse switching can be performed without using the main clutch pedal 40 without operating the clutch. It is.

In order to artificially slide the spline boss 73, the outer ring 7 of the bearing 77 is used.
A clutch fork 89 externally engaged with the clutch fork 7b is slidably loosely fitted on a clutch operation shaft 90 inserted and supported in the transmission case 7, and a cam member 91 and a clutch fork 89 pin-fixed to the clutch operation shaft 90.
A climbing cam portion 92 is formed between the boss portion 89a and the boss portion 89a. Further, the outer end of the clutch operation shaft 90 and the main clutch pedal 40 are linked and linked, and when the main clutch pedal 40 is depressed to rotate the clutch operation shaft 90, as shown in FIG. The cam member 91 is forcibly rotated with respect to the non-rotatable clutch fork 89 by the engagement of the clutch fork 89, and the clutch fork 89 is relatively slid to the right in the drawing by the cam action of the climbing cam portion 92. A clutch disengagement condition is provided.

The main clutch C is provided with a brake mechanism B having the following structure. That is, the outer ring 77b of the bearing 77 externally fitted to the spline boss 73 is externally fitted with a brake member 94 which is axially opposed to the ring member 93 fixedly connected to the end of the clutch drum 72, After the bearing 77 is moved in the clutch disengaging direction together with the spline boss 73 by the clutch fork 89 to bring the clutch off, the bearing 77 is further moved in the clutch disengaging direction. By contacting the ring member 93 and strongly pressing the brake member 94 against the ring member 93 via the clutch fork 89, a friction braking action is given to the clutch drum 72 from which power transmission is cut off, and Will stop.

That is, the non-rotatable clutch fork 89
Is in frictional contact with the outer ring 77b of the bearing 77, the brake member 94 is in frictional contact with the outer ring 77b, and further, the brake member 94 is in frictional contact with the ring member 93 of the clutch drum 72. The rotation of the clutch drum 72, which is a rotating member, is indirectly braked by the clutch fork 89.

In the above example, the clutch drum 72 is indirectly frictionally braked by the clutch fork 89. However, in the main clutch disengaged state, the clutch drum 72, which is a rotating member on the driven side of the main clutch C, or is connected thereto. It is also possible to connect a portion directly contacting the ring member 93 to the clutch fork 89.

[Brief description of the drawings]

FIG. 1 is an overall side view of a riding rice transplanter.

FIG. 2 is a schematic diagram of a traveling transmission system.

FIG. 3 is a sectional view showing a part of a transmission case.

FIG. 4 is a cross-sectional view showing the main clutch in a clutch engaged state.

FIG. 5 is a sectional view showing the main clutch in a clutch disengaged state;

FIG. 6 is a schematic diagram of a traveling transmission system in a first example of another embodiment.

FIG. 7 is a schematic plan view showing a traveling system according to a first example of another embodiment.

FIG. 8 is an exploded side view of a pedal operation unit according to a first example of another embodiment.

FIG. 9 is a sectional view showing a part of a transmission case according to a second example of another embodiment.

FIG. 10 is a sectional view showing a main clutch and a forward / reverse switching mechanism according to a second example of another embodiment;

FIG. 11 is a sectional view showing a main clutch in a clutch engaged state according to a second example of another embodiment.

FIG. 12 is a sectional view showing a main clutch in a clutch disengaged state according to a second example of another embodiment.

[Explanation of symbols]

 Reference Signs List 1 front wheel 2 rear wheel 15 differential mechanism 26 side brake 41 driven-side rotating member (ring member) 43 brake member 68 differential mechanism 72 driven-side rotating member (clutch drum) 89 clutch fork C main clutch G2 driven-side rotating member ( gear)

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Shinsuke Kotani 64 Ishizu-Kitacho, Sakai-shi, Osaka F-term in Kubota Sakai Works (reference) 3D052 AA11 BB12 BB13 BB14 BB18 DD03 EE02 EE03 FF01 GG03 HH01 JJ02 JJ08 JJ11 JJ11 JJ12 JJ17 JJ20 3J058 AB34 BA17 CC08 CC66 CC76 CD30 FA13

Claims (5)

[Claims] In a paddy field working machine configured to drive left and right front wheels and rear wheels via an engine power via a main clutch, and a left and a right rear wheel respectively provided with side brakes, a disengagement operation of the main clutch is performed. A paddy working machine characterized by comprising a brake means for applying a braking action to a traveling transmission system on the lower transmission side from the main clutch in conjunction with the main clutch. 2. The left and right front wheels are driven via a differential device,
The paddy field working machine according to claim 1, wherein the left and right rear wheels are configured to be driven via a side clutch and the side brake, and the side brake is configured to be braked by an operation subsequent to a disengagement operation of the side clutch. . 3. The main clutch is constituted by a multi-plate clutch, and the brake means is moved to a non-rotatable brake member in accordance with the operation of the main clutch operating member being moved to the clutch disengagement side. The paddy working machine according to claim 1, wherein the paddy field working machine is configured to be held between the pair of rotating members. 4. The main clutch is constituted by a multi-plate clutch, and the brake means is indirectly or directly abutted and pressed between a clutch fork for operating the main clutch and a clutch fork moved to a clutch disengagement side. 2. The paddy field working machine according to claim 1, wherein said paddy field working machine comprises a driven side rotating member and said clutch fork applies frictional braking to said driven side rotating member in a main clutch disengaged state. 5. The paddy field working machine according to claim 1, further comprising a clutch disengagement locking means for fixing the main clutch in a disengaged state.