JPH04266532A - Operation device for working vehicle - Google Patents

Abstract

PURPOSE:To perform stable operation control during the work of a working vehicle. CONSTITUTION:In an operation device for a working vehicle 5 wherein a speed control lever 3 to continuously variably control the speed of a working vehicle is rotatably mounted on a handle 1 for the vehicle, a speed fine regulating member 4 interlocking with the control lever 3 is located in the vicinity of a grip 6 of the handle 1. Rough regulation of a speed is effected by means of the control lever 3 and fine regulation of a speed is effected by a part of the fingers of a hand grasping the handle grip 6.

Description

[Detailed description of the invention]

0001

[Industrial Application Field] The present invention is applicable to lawn mowing, grass cutting, tilling,
This invention relates to operating devices for work vehicles such as snow removal.

0002

2. Description of the Related Art A conventional operating device for a work vehicle of this type is disclosed in Japanese Patent Laid-Open No. 1-202541. While driving, one hand grips the handle grip, and the other hand leaves the handle grip and grips the gear shift lever.

0003

However, if such an operating device is immediately applied to a one-wheel work vehicle, there is a risk that the work efficiency and work accuracy will be reduced because the machine body will be unstable. In other words, a single-wheeled work vehicle has only one wheel positioned on the frame center, so it is less stable than a two-wheeled or four-wheeled work vehicle, so workers must hold the handle grips with both hands. You have to drive while keeping your balance. Therefore, if the user grips the handle grip with only one hand and operates the gear shift lever with the other hand removed from the handle grip, it becomes difficult to maintain the balance of the one-wheeled work vehicle. These problems also exist in two-wheeled work vehicles, although to varying degrees.

The present invention was devised to solve these problems, and an object of the present invention is to provide a convenient operating device for a work vehicle that allows stable work to be performed.

[0005]

[Means for Solving the Problems] In order to achieve this object, the present invention provides a working vehicle in which a speed control lever for controlling the speed of the vehicle is rotatably attached to the handle of the working vehicle. The operating device is characterized in that a speed fine adjustment member interlocked with the control lever is provided near the grip portion of the handle.

[0006]

[Operation] In the above configuration, after determining the rough speed with the control lever, the driver operates the speed fine adjustment member using part of the fingers of one hand without removing both hands from each handle grip. Since the other part of the fingers of one hand is still grasping the handle grip, it is possible to balance the work vehicle with both hands and select the appropriate speed to perform the work. can.

[0007]

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below in detail with reference to the drawings.

FIG. 1 is a partially cutaway plan view of an operating device for a working vehicle according to the present invention, and FIG. 2 is a longitudinal cross-sectional view of the same operating device, in which 1 is a handle, 2 is a bracket, 3 is a speed control lever, and 4 is a vertical sectional view of the same operating device. is a speed fine adjustment member.

The handle 1 consists of a pair of rod-like bodies whose base ends are fixed to the left and right sides of a handle column 1' fixed to the upper part of the transmission case of a single-wheeled tiller 5 (FIG. 4) and extend rearward, respectively. A grip 6 is attached to the rear end, and a bracket 2 is fixed to a handle portion near the left grip 6 so as to bulge inward.

The bracket 2 consists of a main body part 7 welded to the handle 1 and a cover part 9 fixed to the main body part 7 with bolts 8 and nuts 14. The speed control lever 3 passes through the cover part 9. Moreover, the elongated hole 10 that guides the lever 3 back and forth is on the inside (right side), and the notch 11 from which the speed fine adjustment member 4 partially protrudes is on the outside (left side).
There are holes in each side. The bracket 2 is provided with shafts 12 and 13 that support the speed control lever 3 and the speed fine adjustment member 4, respectively, and an intermediate gear 63 that interlocks and connects the speed control lever 3 and the speed fine adjustment member 4. An intermediate shaft 15 that loosely fits and supports is installed.

A shaft 12 supporting the speed control lever 3 is fitted with a mounting frame 16 at the base end of the lever 3 on the inside, and a collar 17 and a plurality of friction plates 18 are sequentially mounted outward from the mounting frame 16. Furthermore, a fan-shaped gear 20 is fitted through the cylindrical shaft 19, and two disc springs 21 and a collar 2 are fitted on the outside of the sector-shaped gear 20.
2 are fitted in sequence, and the outermost part is held down by the umbrella part 23 of the shaft 12, while one end is tightened to the mounting frame 16 with a nut 24. Therefore, the speed control lever 3 and the sector gear 20 are held in their normal positions by the tightening force of the nut 24, the biasing force of the disc spring 21, and the frictional force of the friction plate 18.

The speed control lever 3 has its base end connected to the mounting frame 16.
A knob 25 is fitted to the distal end thereof, and one end of an inner wire 27 of the speed change wire 26 is connected to the mounting frame 16. The other end of the wire 27 is connected to, for example, a hydrostatic continuously variable transmission (hereinafter abbreviated as "HST").
30 (FIG. 6). And shifting wire 2
One end of the outer wire 28 is fixed to a bracket 29 fixed to the handle 6, and the other end is fixed to a transmission case 47.

As shown in FIG. 6, the HST 30 in this embodiment continuously changes the speed of the power transmitted from the power transmission input shaft 32 (O1) and supplies it to the traveling transmission device 33. Specifically, this is done by changing the inclination angle of the movable swash plate 35 of the hydraulic pump 34 about a rotation axis (not shown). Therefore, the other end of the wire 27 is connected to the movable swash plate 35, and the inclination angle of the movable swash plate 35 can be changed or adjusted by operating the speed control lever 3. The lever 3 is configured such that when tilted forward in FIG. 5, the speed gradually increases, when tilted backward the speed gradually decreases, and when the lever 3 is tilted completely backward, the speed is stopped.

As shown in FIG. 3, the plurality of friction plates 18 are
The friction plate 51 with a tongue piece and the friction plate 52 with a fork piece are arranged so as to overlap alternately, and each tongue piece part 53 is arranged between the cylindrical shaft 19 fitted to the shaft 12 and the disc spring 21. On the other hand, each fork piece portion 56 engages with an engaging piece 55 extending from a disc 54 interposed between the cylindrical shaft 19 and the friction plate 18. It is engaged with the coupling piece 58. The engagement piece 58 further extends and engages with the engagement groove 59 of the mounting frame 16. Reference numeral 75 denotes a stopper projecting from the outer periphery of the disc 54, and is adapted to be engaged with the bracket body portion 7.

The fan-shaped gear 20 has a main tooth portion 60 facing rearward and meshes with a small-diameter gear 61 portion of an intermediate gear 63 having a small-diameter gear 61 and a large-diameter gear 62. The large diameter gear 62 portion of the intermediate gear 63 is connected to the small diameter gear 64.
The small diameter gear 64 of the speed fine adjustment member 4 having the large diameter fine adjustment knob 65 meshes with the small diameter gear 64 portion thereof. Further, a locking boss 20 is provided in one piece at right angles toward the inner wall of the fan-shaped gear 20.
a, 20b, and 20c are respectively fitted into engagement grooves 57a, 57b, and 57c provided in a disc 57 that engages with the friction plate 18, and the sector gear 20, intermediate gear 63, and speed fine adjustment member are used to move the lever 3. 4 is linked and follows the structure.

The shaft 13 of the speed fine adjustment member 4 is installed at the rear inside the bracket 2 closest to the handle grip 6, and its large diameter fine adjustment knob 65 is connected to the notch 11 of the cover 9.
It protrudes upwardly from the rear and faces near the handle grip 6, and is located within the reach of a part of the fingers of the hand gripping the handle grip 6, so that it can be rotated by the fingers.

In FIG. 3, 66 is a color, and 67 is a color.
is a washer, 68 is a stopper pin, and 69 is a cap of the knob 25.

In FIG. 6, 36 is a component of the hydraulic pump 34, and is a continuously variable input shaft (O8) connected to the power transmission input shaft 32, and a cylinder block 37 is connected around the input shaft 36. is fixed, a plurality of plunger holes 38 are bored in the cylinder block 37, a plunger 39 is accommodated in each plunger hole 38, and the outer end of each plunger 39 slides in contact with the movable swash plate 35. It is designed to rotate. This rotation operates oil in an oil passage (not shown) formed in the substrate 40 to rotate the hydraulic motor 41.

The hydraulic motor 41 has an output shaft 4 for continuously variable transmission.
2 (O2), a cylinder block 43 fixed around the output shaft 42, a plurality of plunger holes 44 bored in the cylinder block 43, and a plunger 45 accommodated in each plunger hole 44, It consists of a fixed swash plate 46 provided on the outer end side of each plunger 45, and the plunger hole 44 communicates with the oil passage. A gear G2 is fixed to the end of the continuously variable transmission output shaft 42 facing into the mission case 47, and the gear G2 meshes with a gear G3 fitted to the starting end shaft O3 of the traveling transmission device 33. There is.

The power transmitted to the gear G3 is transmitted from the shaft O3→
Through a path formed in the order of gear O4 → gear G6 → shaft O4 → gear G8 → gear G9 → shaft O5 → sprocket S1,
Or, shaft O3 → gear O5 → gear G7 → shaft O4 → gear G
The power is transmitted to the running wheels 48 (FIG. 5) through paths formed in the order of 8→gear G9→sprocket S1 as forward or reverse rotational power.

[0021] Reference numeral 49 is a working transmission in which the power is transmitted immediately from the input shaft O1 without going through the HST30, and the gear O1 → gear G10 → shaft O6 → gear G11 → gear G12 → shaft O7 → sprocket S4. 4 by the speed change gear path formed in this order, or by the speed change gear path formed in the order of gear O1 → gear G10 → shaft O6 → sprocket S2 → chain C → sprocket S3 → shaft O7 → sprocket S4. , is interlocked and connected to a rotary 50 of a one-wheel type tiller shown in FIG.

4 and 5, 70 is an engine, 71 is a main clutch lever, 72 is a main clutch, 73 is a transmission belt, and 74 is a power transmission pulley. In addition, 76 is a forward/backward switching lever, which moves forward when rotated upward and moves backward when rotated downward.
is a rotary forward/reverse lever.

Next, the operation of the embodiment configured as described above will be explained.

Now, assuming that the one-wheel type cultivator shown in FIG. When connected,
Power is transmitted to the power transmission input shaft 32 of FIG. 6 via the transmission belt 73 and the power transmission pulley 74, and is distributed from the input shaft 32 to the work transmission 49 side and the traveling transmission device 33 side.

In the work transmission 49, by rotating the rotary forward/reverse lever 77 in the forward direction, the power input from the transmission pulley 74 is transferred from shaft O1 → gear G1 → gear G10 → shaft without passing through HST 30. O6→Gear G1
1→gear G12→shaft O7→sprocket S4 as forward rotation system power, and by rotating the lever 77 in the opposite direction, shaft O1→gear G1→gear G10→shaft O6→sprocket S2→chain C→Sprocket S
3→shaft O7→sprocket S4 and are transmitted to the rotary 50 as reverse rotational power.

On the other hand, in the traveling transmission device 33, the power input from the transmission pulley 74 and transmitted in the order of shaft O1 → shaft O9 → shaft O8 is transmitted according to the degree of tilting of the speed control lever 3 while passing through the HST 30. Also, the speed is changed steplessly according to the degree of rotation of the speed fine adjustment member 4, and this speed change power is transferred from shaft O2 → gear G2 → gear G3 → shaft O3 → gear G4 → gear G.
6 → shaft O4 → gear G8 → gear G9 → shaft O5 → sprocket S1, or
of the forward/reverse switching lever 76 through a transmission gear system formed in the order of shaft O2 → gear G2 → gear G3 → shaft O3 → gear G5 → gear G7 → shaft O4 → gear G8 → gear G9 → shaft O5 → sprocket S1. The power is transmitted to the traveling wheels 48 as power for forward rotation when the lever 76 is rotated upward, or for reverse rotation when the lever 76 is rotated downward.

At that time, the power for forward or reverse rotation is obtained by tilting the speed control lever 3 shown in FIGS.
This can be achieved by roughly changing the inclination angle shown in FIG. 6) and by rotating the speed fine adjustment member 4 to finely change the inclination angle.

Specifically, by operating the speed control lever 3 and the speed fine adjustment member 4, as shown in FIG. Let it work. That is, in FIG. 6, when the pump shaft, that is, the continuously variable transmission input shaft O8 rotates, the cylinder block 3 of the hydraulic pump 34 rotates integrally with it.
7 also rotates, and each plunger 39 fitted into the plurality of plunger holes 38 of this cylinder block 37 reciprocates, but the stroke of the reciprocating movement of the plunger 39 is determined by the inclination angle of the movable swash plate 35. . for example,
The larger the inclination angle, the greater the oil flow rate of the pump, the more oil is sent to the hydraulic motor 41 through a high-pressure oil path (not shown), and the rotational speed of the motor shaft, that is, the continuously variable transmission output shaft O2, increases. The oil used for the rotation is sent from the hydraulic motor 41 to the hydraulic pump 34 through a low-pressure oil path (not shown).

Since the hydraulic motor 41 has a fixed swash plate 46, when oil is introduced from the hydraulic pump 34 side, the oil acts on the plunger 45 there and presses the fixed swash plate 46, so that the swash plate 46 is fixed. This sliding movement rotates the cylinder block 43 housing the plunger 45, and thus rotates the continuously variable transmission output shaft O2 that is integrally fitted with the cylinder block 43. The rotation speed increases as the amount of oil increases.

Therefore, the running wheels 48 connected to the continuously variable transmission output shaft O2 travel while being continuously changed in speed by the HST 30.

At this time, for example, when adjusting the stroke of the reciprocating motion of the plunger 39 of the hydraulic pump 34 to increase the speed, first adjust the approximate inclination angle of the movable swash plate 35 by tilting the speed control lever 3 forward. is set, and then the inclination angle of the movable swash plate 35 is finely adjusted using the speed fine adjustment member 4, whereby the inclination angle of the movable swash plate 35 is properly set.

First, when tilting the speed control lever 3 forward, the left hand leaves the left handle grip 6 and grips the lever knob 25 to rotate the control lever 3 in either the forward or backward direction. At that time, the control lever 3 is attached to a mounting frame 16 along the elongated hole 10 and having the shaft 12 as a pivot.
The movable swash plate 35 rotates against the biasing force of the disc spring 21 and the friction force of the friction plate 18, and pulls the inner wire 27, causing the movable swash plate 35 to roughly tilt forward about a rotation axis (not shown). When the control lever 3 stops rotating, the mounting frame 1
6 is clamped by the nut 24 and the collar 17 due to the biasing force of the disc spring 21, the frictional force of the friction plate 18, etc. and comes to rest, so the movable swash plate 35 also comes to rest in its roughly tilted state. In this state, continuously variable speed is performed by the HST 30, and the running wheels 48 travel. In this way, the rough running speed is first selected, and then the left hand is returned to the left handle grip 6, and the left and right handle grips 6 are gripped with each hand to maintain balance while plowing and leveling the land. Continue. At this time, grip the handle grip 6 with some fingers of the left hand, and place the fingers of that hand on the fine adjustment knob 65.

Subsequently, when operating the fine adjustment knob 65, force is applied forward or backward to the fine adjustment knob 65 with the finger placed on the fine adjustment knob 65.

Now, when a forward force is applied to the fine adjustment knob 65, the small diameter gear 64 integrated with the knob 65 rotates counterclockwise (counterclockwise) as shown in FIG. The gear 62 is rotated clockwise, and the small diameter gear 6 is integrated therewith.
Rotate the sector gear 20 meshing with 1 counterclockwise,
This and the engaging piece 5 are integrated by the clamping force.
The control lever 3 integrated through the lever 8 is rotated counterclockwise, and the inner wire 27 connected to the mounting frame 16 of the lever 3 is pulled.

At this time, the fan-shaped gear 20 and the control lever 3 are connected to a disk 57 in which locking bosses 20a, 20b, and 20c, which are integrally provided at right angles toward the inner wall of the fan-shaped gear 20, are engaged with the friction plate 18. The fan-shaped gear 20, the intermediate gear 63, and the speed fine adjustment member 4 are interlocked with and follow the movement of the lever 3, so that the fan-shaped The torque of gear 20 is controlled by control lever 3.
and the control lever 3 is controlled by the engagement between the engagement piece 58 and the engagement groove 59, the engagement of the locking bosses 20a, 20b, 20c into the engagement grooves 57a, 57b, 57c, etc. It is reliably held in the rotated position by the clamping force of the disc spring 21 and the nut 24, the frictional force of the friction plate 18, etc.

Therefore, the inclination angle of the movable swash plate 35 connected to the inner wire 27 can be finely tilted.

Conversely, when a backward force is applied to the fine adjustment knob 65, a rotational force in the opposite direction to that described above is generated, the inner wire 27 is loosened, and the tilt angle of the movable swash plate 35 is slightly tilted in the opposite direction. obtain.

The inclination angle of the movable swash plate 35 using the fine adjustment knob 65 can be finely tilted both during forward and backward movement of the tilling operation. As a result, the continuously variable transmission of the HST 30 is finely adjusted.

As described above, according to this embodiment,
Since the rotational speed of the wheels 48 can be adjusted to a constant constant according to the load applied to the rotary 50 without losing balance, stable tillage is possible, the grain size of the tilled soil is uniform, and the tillage depth is also constant, thus improving tillage. Efficiency and accuracy of land leveling work will be improved.

[0040] In the above embodiment, an example was described in which the present invention was applied to a tiller, but it may also be applied to other work vehicles such as a lawn mower, a grass cutter, a snow blower, etc., and the same effect can be obtained. It is effective.

[0041]

As described above, the present invention provides an operating device for a work vehicle in which a speed control lever for controlling the speed of the vehicle in a stepless manner is rotatably attached to the handle of the work vehicle. The present invention is characterized in that a speed fine adjustment member linked to the control lever is provided near the grip portion of the handlebar, so that even if a work load or the like occurs while driving, the operator can maintain the posture of gripping the handlebar with both hands. By manipulating the material of the speed fine adjustment part with some fingers, it is possible to respond to load fluctuations, and work can be performed stably from beginning to end, improving work efficiency and work accuracy.

[Brief explanation of the drawing]

FIG. 1 is a partially cutaway plan view of an operating device for a work vehicle according to the present invention.

FIG. 2 is a longitudinal sectional plan view of the operating device of the work vehicle.

FIG. 3 is an exploded perspective view of essential parts of the operating device of the work vehicle.

FIG. 4 is a plan view of a one-wheel type tiller equipped with the same operating device.

FIG. 5 is a side view taken along line V-V in FIG.

FIG. 6 is a sectional view taken along the line VI-VI in FIG. 4;

[Explanation of symbols]

1 Handle 3 Control lever 4 Fine adjustment member 5 Work vehicle (tiller) 6 Handle grip 63 Dial (knob)

Claims (2)

[Claims] 1. An operating device for a work vehicle, in which a speed control lever for controlling the speed of the vehicle in a stepless manner is rotatably attached to the handle of the work vehicle, wherein a speed control lever is provided near a grip portion of the handle and interlocks with the control lever. An operating device for a work vehicle, characterized in that a speed fine adjustment member is provided. [Claim 2] The speed fine adjustment member is composed of a dial,
2. The operating device for a work vehicle according to claim 1, wherein said dial is operatively connected to a speed control lever via a gear group.