JPH11113317A - Hydraulic control valve of combine harvester or the like - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable high changeover response of each changeover valve of a direction control part, a reaping control part, an unload part or the like at a higher speed than conventional speed in a hydraulic circuit for each control of a combine harvester. SOLUTION: This hydraulic control valve of a combine harvester or the like is constituted by using a pressure changeover valve 4, a direction changeover valve 5 and a vertical changeover valve capable of each responding at a high speed, respectively, in an unload part U for automatically escaping working pressure oil in no-load, a steering control part C capable of controlling direct advance by automatically and laterally steering a machine body and a reaping control part B capable of controlling reaping height by automatically controlling a reaping apparatus in a hydraulic circuit M acting by feed of oil from a hydraulic pump 1.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic control valve such as a combine and the like, and belongs to a field using a switching valve capable of responding at high speed for driving or unloading each actuator in a hydraulic circuit.

[0002]

2. Description of the Related Art Conventionally, in a hydraulic circuit such as a combine or the like, a switching valve for driving an actuator for each operation or a switching valve for unloading, for example, the traveling direction of an airframe is automatically controlled. When the switching response is slow, such as a direction switching valve that steers to the left or right, an up / down switching valve that automatically adjusts the cutting height of the mowing device, and a pressure switching valve that automatically releases working pressure oil when there is no load In addition to the meandering of the aircraft during straight cutting, the work performance is impaired due to uneven cutting height, etc., and due to the operation deviation between the pressure switching valve and the direction switching valve or the vertical switching valve due to the delay in pressure rise, Further, there is a risk that the number of malfunctions will increase.

Accordingly, the present invention aims to improve the work performance by enabling the switching response of each of these switching valves to respond at high speed.

[0004]

According to the present invention, there is provided a hydraulic circuit M operated by oil supply from a hydraulic pump 1 in an unloading section U for automatically releasing operating pressure oil when there is no load.
High-speed response to a steering control unit C capable of automatically moving the body 2 left and right to control straight ahead and a cutting control unit B capable of automatically adjusting the cutting device 3 up and down to control the cutting height. A hydraulic control valve such as a combine is characterized by using a simple pressure switching valve 4, a direction switching valve 5, and a vertical switching valve 6.

[0005]

According to the above configuration, a hydraulic circuit M such as a combine or the like is provided.
In the steering control unit C, the left and right traveling clutches are disengaged by the action of the direction switching valve 5 by arranging the direction switching valve 5 capable of responding faster than usual by, for example, three-port two-position switching for each of the left and right. The traveling brake can be braked to control the traveling direction of the machine body 2 in a straight line stably, and the reaping control unit B can raise and lower the reaping device 3 separately, for example, at a higher speed than normal by switching between two ports and two positions. By arranging the responsive up / down switching valve 6, the action of the up / down switching valve 6 can maintain and control a constant cutting height. In addition, by disposing a pressure switching valve 4 capable of responding faster than usual by, for example, two-port two-position switching in the unloading section U, the action of the direction switching valve 5 or the up / down switching valve 6 by the pressure switching valve 4 is achieved. The pressure can be quickly increased according to the pressure.

[0006]

As described above, in the hydraulic circuit M such as a combine or the like, the direction switching valve 5 of the steering control unit C for controlling the body 2 left and right to control the straight traveling, and the cutting height of the cutting device 3 are kept constant. Response of the up-down switching valve 6 of the cutting control unit B and the pressure switching valve 4 of the unloading unit U that raises the pressure when the directional switching valve 5 or the up-down switching valve 6 is actuated. Directional switching valve 5
In the case of the action of, the meandering and streaking of the machine body 2 when cutting straight ahead is prevented, and when the up-and-down switching valve 6 is operated, poor threshing performance and the like caused by uneven cutting height of the cutting device 3 are prevented. Since it is possible to prevent troubles or the like caused by a delay in pressure rise of the pressure switching valve 4 when the switching valve 5 or the up / down switching valve 6 is operated, switching responsiveness and smooth operation can be improved.

[0007]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 12 shows the overall structure of the combine, and a traveling device 9 having a pair of left and right traveling rollers 8 traveling on the soil surface below the traveling frame 7 of the body 2.
And threshing the harvested culm supplied by being fed and held by the feed chain 10 on the traveling frame 7;
A threshing device 13 including a grain tank 11 for selectively collecting the threshed kernels and temporarily storing the threshed kernels, and a threshing auger 12 for discharging the stored kernels to the outside of the machine is mounted.

In front of the threshing device 13, a weeding body 14 for weeding the planted grain culm from the front end side thereof, a raising portion 15 for producing the weeded grain culm, and a cutting blade for cutting the caused grain culm. A cutting cylinder 3 driven by a hydraulic drive, comprising a cutting section 3 having a section 16 and a grain culm transfer section 17 for transferring the cutted culm to the feed chain 10 while transferring the cut culm rearward to the feed chain 10. 18 is arranged so as to be able to move up and down on the soil surface.

An operation device 19 for controlling the operation of the combine is provided on one side of the reaper 3 and an operation seat 20 for this operation.
An engine 21 is mounted below the operation seat 20, the Glen tank 11 is disposed on the rear side, and a cabin 22 that covers the operation device 19 and the operation seat 20.
Is provided. The traveling device 9, the threshing device 13, the mowing device 3, the operating device 19, the engine 21, and the like constitute the combine body 2.

At the rear side of the weeding body 14 on the left end side, direction sensors 23 are provided with left and right rotatable detection rods 23a for detecting the advancing direction of the body 2 by contacting the uncut culms. At the same time, a cutting height sensor 24 that emits an ultrasonic wave and receives the reflected wave to detect the cutting height of the cutting culm is disposed on the rear side of the grass plant 14. A front-rear inclination sensor 25a and a left-right inclination sensor 25b of a capacitance type for detecting the front-rear and left-right inclination of the body 2 are arranged at appropriate positions on the traveling frame 7, respectively.

The gear transmission mechanism of the traveling transmission case 26 mounted on the front end side of the traveling frame 7 will be described separately for two systems. First, as shown in FIGS. 2A and 3, an input gear 29 fixed to an input shaft 28 of a first shaft, which is input from a hydraulic stepless motor 27, and a transmission shaft 3 of a second shaft.
0 is meshed with an input transmission gear 31 which is axially stopped at the left end of the transmission gear 30.
And a high-speed drive gear 32b meshingly connected to a clutch pawl 32a on the side surface of the shift drive gear 32.
To the right end of the speed change shaft 30. The high-speed drive gear 32b is meshed with a high-speed gear 34a that is fixed to the right end of the third shaft 33, and the high-speed gear 34a
The third-speed sub-shift is constituted by interlocking and linking the medium-speed gear 34b and the low-speed gear 34c, which are fixed at appropriate intervals on the left side, with the speed-change drive gear 32, respectively.

The low-speed gear 34b and a steering center gear 36, which is fixed to a steering shaft 35 of a fourth shaft, are meshed and linked, and left and right steering clutches 37 meshed and connected to both side surfaces of the steering center gear 36, respectively. The left and right steering clutches 37 are provided with a gear portion 37a, a shifter groove portion 37b and a boss portion 37c from the steering center gear 36 side, and the left and right shifter groove portions 37b. The left and right steering shifters 39 that slide the steering clutch 37 left and right by hydraulically driven left and right steering cylinders 38 are engaged with the left and right hydraulically driven brake cylinders 4 on the left and right boss portions 37c.
The left and right traveling brakes 41, which are braked by 0, have their rotating disc sides fixed to the shaft, and the stop disc side is fixed to the inner wall.

Right and left gear portions 37a of the steering clutch 37
And two left and right steering transmission gears 43, which are idlely supported on a fifth shaft reduction shaft 42, are respectively meshed and linked, and the other small diameter gear 43a of the steering transmission gear 43 and the left and right of the sixth shaft The left and right wheel gears 45 fixed to one end of the wheel shaft 44 are engaged with each other, and the left and right drive wheels 46 for driving the traveling crawler 8 are fixed to the other end of the wheel shaft 44, respectively. Let it.

Next, as shown in FIGS. 2 (b) and 3, the input shaft 28 of the first shaft passes through the speed change shaft 30 of the second shaft and the third shaft 30.
The transmission path as described above extends to the counter shaft 33 of the shaft, but a spin turning gear 47a on one side of a turning switching gear 47 that slides on one end of the counter shaft 33, and
A spin intermediate gear 49 fixed to one end of a turning intermediate shaft 48 of the seventh shaft is meshed with and linked to a spin intermediate gear 49, and a spin drive gear 50 fixed to the right side of the spin intermediate gear 49 at an appropriate interval.
And a revolving gear 52 fixed to a revolving shaft 51 of the eighth shaft.

The turning gear 47b on the other side of the turning switch gear 47 of the third shaft and the turning gear 52 of the turning shaft 51 are meshed and interlocked with each other. The left and right turning drive gears 55 fixed to the boss portion 54a extending inward from the stop disc side while the left and right turning clutches 54 actuated by the cylinder 53 are axially stopped. The steering transmission gear 43 is meshed and linked.

As shown in FIG. 4 and FIG. 5, a left and right rolling metal 57 fixed to the center of the running frame 7 in the vertical direction and provided at the lower front part of the left and right vertical frames 56 has a front part. The rolling arm 58 is rotatably supported, and the lower end positions of the left and right front rolling arms 58 and the front sides of the left and right wheel frames 59 located outside and below the left and right vertical frames 56, respectively. The position and the position are rotatably connected.

Pitching shafts 61 are attached to left and right pitching metals 60 provided at the rear lower portions of the left and right vertical frames 56, respectively.
Are rotatably supported, and left and right pitching arms 62 are fixed to the left and right sides of the pitching shaft 61, respectively. The left and right pitching arms 62 and the H-shaped connecting arms 6 in plan view.
3 is rotatably connected to one end on the left and right sides, and the other end is rotatably connected to the left and right rear rolling arms 64. And the rear side position of the wheel frame 59 is rotatably connected.

The left and right rear wheels 65 are rotatably supported above the rear ends of the left and right wheel frames 59, respectively, and are provided at predetermined intervals below the outer surfaces of the left and right wheel frames 59, respectively. A plurality of grounding wheels 66 are freely rotatably supported at
These left and right rear wheels 65 and a plurality of ground wheels 66
And driving wheels 46 for transmitting power from a traveling transmission case 26 mounted on the front end of the traveling frame 7.
The left and right traveling rollers 8 are wound around each other.

At the upper end of the right pitching arm 62,
The movable front ends of the pitching cylinders 67 driven by hydraulic pressure are connected, and the left and right front rolling arms 58 and the left and right rear rolling arms 64 are rotated by left and right connecting rods 68 so as to form four-point parallel links. To the upper end of the left and right rear rolling arms 64 extending further upward from the connecting position of the connecting rod 68,
The movable tip portions of the left and right rolling cylinders 69 driven by hydraulic pressure are connected to each other.

Thus, the left and right front and rear rolling arms 58, 64 and the left and right rolling cylinders 6 are provided.
9 and the like, a horizontal control means by rolling control for raising / lowering or tilting the body 2 horizontally is constituted, and the pitching arm 62 and the pitching cylinder 67 are formed.
By such operations, a front-rear horizontal control means by pitching control for tilting the body 2 back and forth is configured.

During the harvesting operation in such a combine, detection of the traveling direction of the body 2 by the direction sensor 23,
The detection of the cutting height of the cutting device 3 by the cutting height sensor 24 and the detection of the horizontal state of the body 2 by the front and rear and left and right inclination sensors 25a and 25b, as shown in FIG. B, a horizontal control unit T, an unloading unit U, etc., and a hydraulic circuit M for operating the same.

The steering control unit C in the hydraulic circuit M is provided with a hydraulic pump 1 from the oil tank 70 of the hydraulic stepless irregularity device H or the like.
Via the priority diversion valve 71 by switching the three-port two-position by changing the spool stroke, shape, etc., the three-port two-position that can respond faster than normal switching response speed of the valve A left and right direction switching valve 5 for electromagnetically switching between the left and right direction switching valves 5 is connected to left and right steering cylinders 38 which respectively turn on and off the steering clutch 37 by left and right steering shifters 39. .

Through the left and right steering cylinders 38, the left and right brake cylinders 40 for respectively braking the left and right traveling brakes 41 by the left and right operation switching valves 72 for electromagnetically switching the four-port and two-positions, and spin rotation or mild rotation. The left and right turning cylinders 53 for turning the left and right turning clutches 54 are arranged so as to be switchable, and from the middle between the left and right steering cylinders 38 and the left and right action switching valves 72 via check valves 73 respectively. The relief valve 74 is connected to a relief valve 74 for manual control by a power steering lever 74a.
4 to the oil tank 70 so as to be returned.

The cutting control unit B changes the valve stroke response and the shape through the priority diverting valve 71 and the throttle valve 75a to change the response speed of the switching of the valve. The up / down switching valve 6a of the up / down switching valve 6 is connected to the lifting / lowering cylinder 18 and the lowering switching valve 6b is connected to the down switching valve 6b via the throttle valve 75b. The lower switching valve 6b is connected to return the oil to the oil tank 70.

The unloading section U is connected to the spool by changing the stroke or shape of the spool via the priority branch valve 71.
An amplification valve 76 capable of supporting a large flow rate is connected to a pilot pressure switching valve 4 for electromagnetically switching a 2-port 2 position capable of responding faster than normal switching response speed of the valve. The oil tank 70 is connected to return oil.

The horizontal control unit T includes a pitching switching valve 77 for pitching control for electromagnetically switching the four ports and three positions, and a left and right rolling switching valve 78 for rolling control via the priority diverting valve 71, respectively. The pilot check valve 79a is connected from the pitching switching valve 77 to the extension side of the pitching cylinder 67, and the check valve 7 is
9b, and a pilot check valve 80a and a check valve 80b are respectively connected from the left and right rolling switching valves 78 to the extending sides of the rolling cylinder 69.
It is configured to be connected to the shortening side via a pilot check valve 81.

An auger switching valve 82 for electromagnetically switching the four-port, three-position for vertically moving the auger 12 is connected to an auger cylinder 84 via a pilot check valve 83. When the left or right direction switching valve 5 of the steering control unit C is automatically switched to the operating side by the detection of the direction sensor 23, first, the steering cylinder 38 is operated, and the steering clutch 37 is operated by the steering shifter 39. When the action switching valve 72 is switched to the brake cylinder 40 side with this cut, the traveling brake 41 is braked to perform left-right steering or brake turning when the body 2 goes straight, and the action switching valve When the 72 is switched to the turning cylinder 53 side, the turning clutch 54 is actuated to switch the turning switching gear 47 to perform turning control by spin turning or mild turning.

When the up-switching valve 6a or the down-switching valve 6b of the up / down switching valve 6 of the cutting control unit B is automatically switched to the operation side by the detection of the cutting height sensor 24, each throttle valve 75
a or 75b to adjust the flow rate,
Is operated to raise or lower the cutting device 3 to control the cutting height. When the direction switching valve 5 in the steering control unit C or the up / down switching valve 6 in the reaping control unit B is switched to the operating side, the pressure switching valve 4 of the unloading unit U automatically raises the pressure. To stop the escape of the high-pressure hydraulic oil by the amplification valve 76,
At this time, the response speed of the valve switching of the pressure switching valve 4, the directional switching valve 5, and the up / down switching valve 6 is made to respond faster than usual, so that the pressure rises and switches quickly, and the meandering and the meandering at the time of straight forward cutting are performed. It is possible to prevent stripping and the like, and it is possible to prevent variations in culm length and the like due to uneven cutting height.

In the horizontal control section T, a circuit as shown in FIGS. 6A and 6B can be formed in order to improve the switching response of the left and right rolling switching valves 78 for performing the rolling control. However, since these circuits have a large number of outputs (electricity) to be simultaneously controlled, there is a problem that the electric capacity of the controller must be increased and the controller itself must be increased.

Therefore, as shown in FIG. 7, the left and right rolling switching valves 78 of the horizontal control unit T of the hydraulic circuit M can respond to the switching response speed of the valve faster than usual by changing the stroke and shape of the spool. By replacing the three-port two position with the rolling switching valve 85 for electromagnetically switching, the responsiveness of the left-right horizontal control of the body 2 and the smoothness of the operation can be improved.

As shown in FIG. 8, when the control flow a and the surplus flow b are diverted by the priority diverting valve 71 of the hydraulic circuit M, the steering control unit C is connected to the diverted control flow a. The unloading section U is operated, the cutting control section B and the horizontal control section T are operated on the surplus flow b side, and the control flow a
The switching responsiveness of the left and right direction switching valves 5 of the side steering control unit C and the pressure switching valve 4 of the unloading unit U can be improved by enabling rapid switching of the valves as described above. In addition to this, it is possible to increase the switching frequency and perform high-precision control such as pulse and duty control.

In the hydraulic circuit S as shown in FIG. 9, the left and right direction switching valves 5 of the steering control unit C and the up and down switching valve 6 of the reaping control unit B in the hydraulic circuit M are electromagnetically connected to the four ports and three positions. In addition to replacing the directional switching valve 86 and the up / down switching valve 87 for switching, the directional switching valve 86, the up / down switching valve 87, and the auger switching valve 82 of the waste auger 12 via the priority branch valve 71 from the hydraulic pump 1. A circuit p connected to the unloading pressure switching valve 88a, and another hydraulic pump 89 via the unloading pressure switching valve 88b,
A circuit r connected to the pitching switching valve 77 and the left and right rolling switching valves 78 of the horizontal control unit T is configured separately.

By separating the hydraulic circuit p and the hydraulic circuit r in this manner, a single hydraulic pump 1
It is difficult to perform horizontal control of the body 2 at the time of cutting height control only by oil supply from the, but the horizontal control has been delayed, but it is now possible to simultaneously operate the direction control, the cutting vertical control, and the horizontal control. In addition, the mowing and threshing performance can be improved, and the type can be easily dealt with.

Conventionally, in the hydraulic circuit M, etc., the left and right direction switching valves 5 and up / down switching valves 6 as switching valves for each operation and the pressure switching valve 4 as a switching valve for unloading are simultaneously turned on. , OFF, the rise of the pressure is delayed, the switching response is deteriorated, and the operation is shifted. Therefore, as described above, when switching control is performed by a switching valve capable of responding at high speed, as shown in FIG. 10, the pressure switching valve 4 for unloading is continuously turned on for, for example, 60 ms.
By setting the left and right direction switching valves 5 and the up and down switching valves 6 for each operation to ON state pulses and duty control for 10 ms every 15 ms, for example, each operation is performed by continuously turning on the unloading switching valve. Switching can be performed while the pressure is maintained, so that the response does not deteriorate due to the delay in pressure rise, and the operation deviation due to the variability in the response of each switching valve is also considered. No need to do.

When the hydraulic circuit M performs the straight running control at the time of mowing, the circuit of the steering control unit C is provided only when the traveling speed is equal to or higher than a certain working speed (for example, about 0.8 m / s).
As shown in FIG.
In addition to the control flow a that feeds the oil to the left and right direction switching valves 5 via the control valve 1, a throttle valve is supplied from another hydraulic pump, for example, a charge pump 90 such as a hydraulic type continuously variable transmission H via a supply switching valve 91. Concurrent supply is performed while adjusting the flow rate by 92 and preventing reverse inflow by the check valve 93.

By assisting the pressure oil when the vehicle speed becomes faster than the predetermined speed, even when the switching of each switching valve can be performed at a high speed, it is possible to control the switching time of the valve during harvesting travel. Meandering and out-of-line can be prevented. Although the absolute amount of the control flow a can be increased,
Then, the flow rate of the whole circuit increases, and the capacity of the switching valve needs to be increased, which leads to an increase in cost and an increase in size.

[Brief description of the drawings]

FIG. 1 is a block diagram showing a hydraulic circuit of each working unit of a combine.

FIG. 2A is a front sectional view showing a transmission mechanism of a transmission case in a traveling apparatus. (B) Front view array diagram showing the transmission mechanism of the transmission case in the traveling device.

FIG. 3 is a side array diagram showing a transmission mechanism of a transmission case in the traveling device.

FIG. 4 is a side view showing an elevating mechanism of a traveling crawler in the traveling device.

FIG. 5 is a plan view showing an elevating mechanism of a traveling crawler in the traveling device.

FIG. 6A is a block diagram showing an example of a hydraulic circuit related to the left and right horizontal control of the combine. (B) The block diagram which shows an example of the hydraulic circuit of the left-right horizontal control of a combine.

FIG. 7 is a block diagram showing a hydraulic circuit related to horizontal control of the combine.

FIG. 8 is a block diagram showing a split state of a control flow and a surplus flow in the hydraulic circuit.

FIG. 9 is a block diagram showing a hydraulic circuit in which each work control unit is shared by two hydraulic pumps.

FIG. 10 is a diagram illustrating a continuous ON state of an unload control unit in connection with pulse control of a work control unit.

FIG. 11 is a block diagram illustrating a hydraulic circuit that assists a pressure oil in a direction control unit during high-speed mowing traveling.

FIG. 12 is a side view showing the overall configuration of the combine.

[Explanation of symbols]

 1. Hydraulic pump 2. Airframe 3. Reaper 4. Pressure switching valve 5. Direction switching valve 6. Up / down switching valve Hydraulic circuit U. Unloading section C. Steering control section B. Cutting control unit

──────────────────────────────────────────────────続 き Continued on front page (51) Int.Cl. ⁶ Identification code FI B62D 11/08 B62D 11/08 G

Claims (1)

[Claims] 1. A hydraulic circuit M operated by oil supply from a hydraulic pump 1. An unloading section U for automatically releasing operating pressure oil when there is no load, and a straight-ahead control by automatically steering the body 2 left and right. A pressure switching valve 4, a direction switching valve 5, and a vertical switch that can respond at a high speed, respectively, to a possible steering control unit C and a cutting control unit B that can automatically adjust the cutting device 3 up and down to control the cutting height. A hydraulic control valve such as a combine, wherein the valve 6 is used.