JPS6344328B2 - - Google Patents

Description

[Detailed description of the invention]

The present invention provides a novel self-propelled type that is equipped with a traveling drive unit having a transmission, a reaping unit that reaps planted grain culms, and a threshing unit that threshes and sorts the harvested grain culms. It concerns harvesting machines. The above-mentioned type of self-propelled harvester moves within the field at a speed set by a transmission while reaping the grain culms to be planted in the field with the reaping section, and the harvested grain culms are sent to the threshing section. The grains are transported, and in a threshing section, the grains are threshed from the tip of the grain culm, and sorting is performed in which mixed straw waste is removed from the grains using a sieve, a sorting wind, etc. During harvesting using this type of self-propelled harvesting machine, the operation of the harvesting machine depends on many factors such as maturity, length, lodging and moisture content of the crop, as well as field conditions and type of crop. ruled by. Naturally, during such harvesting operations, it is desirable to perform harvesting operations with high precision and with a small amount of grain lost, and on the other hand, it is desirable to perform harvesting operations with high harvesting speed and high efficiency. This is desirable. Even for experienced workers, it is difficult to carry out harvesting work using self-propelled harvesters while satisfying the contradictory demands of high harvesting accuracy and high harvesting efficiency. . Therefore, the main purpose of this invention is to automatically maintain high accuracy and efficiency in a well-balanced harvesting operation while allowing the harvesting operation to proceed.
Our goal is to provide a new self-propelled harvester. The configuration of the self-propelled harvester according to the present invention and the effects obtained thereby will be explained below with reference to the illustrated embodiments. 1-10 show a first embodiment, and this first embodiment relates to an example in which the present invention is implemented as a combine harvester as shown in FIG. The combine shown in Fig. 1 moves the machine within the field by driving left and right crawlers 1, and divides the grain stalks to be planted in the field using a weed cutting board 2 at the front. The grain culm is raised by a grain culm lifting device 3 which is raised slightly backward from the position of the grass board 2, and the planted grain culm is cut at the base of the plant by a cutting blade 4 located behind the grass dividing board 2. The harvested grain culms are transported toward the threshing section 8 on the machine body by the horizontal conveying belt 5 and the vertical conveying belts 6 and 7 on the stock side and ear side.
The harvested grain culm is conveyed backward by the feed chain 9 along one side, and the tip side of the harvested grain culm is fed into the threshing section 8 for threshing, and the threshed grains are After the sorting, the top suction car 10 on the other side of the fuselage receives the information. Further, in this combine harvester, the feed chain 9 is provided with an extension part 9a extending rearward and upward so that the waste straw leaving the threshing part 8 is carried out by the extension part 9a, and also constitutes a driving source. The engine 11 is mounted on the rear of one side of the fuselage. For convenience of explanation, first, the configuration of the threshing section 8 in the illustrated combine harvester will be briefly explained with reference to FIG.
Inside, there is a handling trunk 13 along the axis in the longitudinal direction of the aircraft.
The handling cylinder 13, which is rotatably provided and driven by the engine 11 through an appropriate transmission mechanism, has a plurality of handling teeth 14 set thereon.
The grains are separated from the tip of the harvested grain culm and threshed. Inside the handling chamber 12, there are also a plurality of dust feeding valves 15 which are supported so as to be adjustable near and far with respect to the handling barrel 13 by rotational displacement, and are dust feeding valves 15 which change and regulate the degree of dust removal from inside the handling chamber 12. A valve 15 is provided. The threshing section 8 is also equipped with a crimp net 16 located below the above-mentioned handling drum 13, and this crimp net 16 collects grains, fine straw waste, etc. from the threshing section onto which the threshing section is dropped. The leakage material is discharged from the dust outlet at the rear end of the crimp net 16. A swing sorting mechanism is provided from the bottom to the rear of the crimp net 16, and includes a feed bun 17 from the front to the rear, a chaff sheave 18 and a grain sheave 19 arranged vertically in parallel, and a stroke rack 20. A winch 21 and a dust exhaust fan 22 are provided at the frontmost and rearmost positions of the inner lower part, respectively. The above-described swinging sorting mechanism 17-20 is made to swing back and forth and up and down, and the feed van 17 at the forefront of the mechanism moves the crimp net 1 along with the swinging.
While transporting the leakage from 6 backwards, heavy grains are sorted to the lower layer and light straw waste etc. to the upper layer. From the grains falling from the feed van 17 to the chaff sieve 18, the sorting wind straw waste sent from the winnower 21 is further removed, and the grains are sorted again by passing through the chaff sieve 18.
A finer grain sieve 19 leaks from the chaff sieve 18, and is fed to the first opening 23 in a carefully selected state by receiving the sorting wind from the winnower 21 during that time. In addition, with the help of Karaki 21 from Feed Van 17, Strollack 20
From the straw waste that is transferred to the top, there is a straw rack 2.
0, the grains mixed in are separated forward and transferred onto the chaff sheave 18,
The ear pieces and some of the grains are separated into a lower layer and fed through the through holes of the stroller rack 20 to the lower second port 24. In the swinging sorting mechanism shown in FIG. 2, an upper stroke rack 25 is provided above the stroke rack 20 described above, and the upper stroke rack 25 is swung to assist the sorting action of the stroke rack 20 described above. At the same time,
Efforts are being made to encourage the removal of straw waste.
The action of the stroke rack 20 itself and the dust removal fan 22
The straw waste leaving the straw rack 20 is
The dust is discharged from the third dust exhaust port 26 toward the rear of the aircraft.
The grains supplied to the first mouth 23 as described above are
The grains are conveyed toward the other side of the machine by the first conveyor 27 in the first mouth 23, and transferred to the top feeder 10 by a frying conveyor (not shown). Further, the ear pieces and the like supplied to the second slot 24 as described above are returned to the handling chamber 12 by the second thrower 28 and are reprocessed within the handling chamber 12. In order to detect the degree of threshing sorting in the threshing section 8, the following sorting degree detector is provided.
That is, in the illustrated case, this detector is configured as a grain loss detector 29 that detects the number of grains contained in the dust discharged from the third dust exhaust port 26, in other words, the amount of grain loss. As shown in FIGS. 2 and 3, the third dust exhaust port 26 is installed to hang down from the upper edge of the dust exhaust end of the third dust exhaust port 26 so as to be inclined rearward and downward. The grain loss detector 29 is equipped with a piezoelectric element 29a such as a piezoelectric ceramic disk, and is configured to output a spike or voltage pulse corresponding to the pressure when it receives pressure. Therefore, when the dust discharged from the third dust exhaust port 26 hits the surface of the detector 29 and receives pressure, the grain loss detector 29 generates a voltage pulse with a frequency and amplitude corresponding to the pressure. Output. Naturally, such voltage pulses will vary as shown in pulses P ₁ and P ₂ shown in FIG. Different frequencies.
4 and 9 to see the sorting status in the threshing section 8 from the amount of lost grains discharged as No. 3 waste.
As shown in the figure, a bandpass filter 30 is provided which is connected to the main body of the Glen loss detector 29 and constitutes a part of the detector 29. As shown in FIG. 4, this band-pass filter 30 filters only the voltage pulse P ₁ with a frequency corresponding to grains, and the voltage pulse P 1 corresponding to straw waste, etc.
_P2 cuts this and does not transmit it to the secondary side. In the illustrated case, the Glenn loss detector 29 is supported in particular as follows. That is, as shown in FIG. 3, a hinge plate 32 is provided on the back surface of the detector 29 by fixing it with a fixture 31.
The above-mentioned hinge plate 32 is rotatably supported by a horizontal pin 35 on a mounting plate 34 fixed to the upper surface with a fixture 33, so that the entire Glen loss detector 29 can be rotated around the horizontal pin 35. It is supported so that it can move freely. In particular, the Glen loss detector 2 rotatably supported as described above.
9 indicates the free end of the hinge plate 32 and the fuselage side frame 3
A tension spring 38 stretched between the support plates 37 on the upper part 6 rotates in the direction of thrusting into the third dust exhaust port 26, that is, in the direction of receiving the wind pressure of the dust exhaust air flowing in the direction of arrow A. has been done. In addition, in the case shown,
A long hole 37a is formed in the support plate 37, and the support plate 37 is fixed to the fuselage side frame 36 by a bolt 39 that passes through the long hole 37a and is screwed into the frame 36. Support plate 3 within the range of
7 positions can be changed to change and adjust the biasing force of the tension spring 38. As shown in FIG. 3 and explained above, the grain loss detector 29 is located at the third dust exhaust port 26, which is a part of the dust exhaust air path, in the direction in which the wind pressure is received. Since the Glen loss detector 29 is rotatably biased by the tension spring 38, the Glen loss detector 29 is rotated when the wind pressure or wind speed and the biasing force by the spring 38 are balanced, as shown in FIG. The grain loss detector 29 is tilted away from the vertical position as the wind speed increases, reducing the area of the wind receiving area. Then, it moves closer to the vertical direction and assumes a posture that increases the area of wind blowing. In this way, the grain loss detector 29 changes the swept area to small or large depending on the magnitude of the wind speed, so even if the wind speed changes, it is proportional to the product V×S of the wind speed V and the swept area S. The amount of dust that comes into contact with the detector surface 29 per unit time is approximately constant, and therefore,
The percentage of lost grains in the waste material is always detected on an approximately constant basis. Further, the grain loss detector 29 is installed at the third dust exhaust port 26 position, and is rotated by a spring 38 during non-operation when no wind force is applied.
As shown by the chain line in the figure, it is automatically stored in the third dust exhaust port 26, thereby preventing inconveniences such as damage from hitting obstacles when the combine is traveling on the road. The attitude of the grain loss detector 29 at this time is regulated by the hinge plate 32 coming into contact with the upper end surface 26a of the dust exhaust port. As shown in FIG. 9, an amplifier 40 is provided connected to the bandpass filter 30 to amplify the voltage pulse P ₁ corresponding to the grain. Furthermore, when a voltage pulse is input from the amplifier 40, it is turned on for a certain period of time,
A monomulti 41 is provided that outputs a rectangular voltage pulse of constant frequency and amplitude. Connected to this monomulti 41, an integrator 42 for integrating the output pulse of the monomulti 41 is provided, and an amplifier 43 is provided connected to this integrator 42. 29, 30, 40-
43 forms a Glen loss detection circuit _C1 . As described above, the degree of threshing sorting in the threshing section 8 can be determined from the amount of grains in the third waste, and the grain loss detection circuit _C1 outputs a voltage signal Vloss proportional to the amount of grains lost at its output terminal. Output. In order to detect the load acting on the threshing section 8, the following threshing load detection circuit is provided. That is, in the illustrated case, this detector is connected to the handling cylinder 13.
As shown in FIG. 2, the handling cylinder rotation detector 44 is installed outside the threshing section 8 on the handling cylinder shaft 13a. This handling cylinder rotation speed detector 44 is connected to the handling cylinder shaft 13 as shown in FIG.
A is provided with a rotor 45 which is fixed to the shaft 13a and rotates integrally with the handling cylinder shaft 13a, and on the inner peripheral surface of the drum-shaped rotor 45, a plurality of magnets 46 are arranged at equal intervals in the circumferential direction. It is fixed. As shown in FIG. 9, the handling cylinder rotation speed detector 44 is further provided with a fixed position reed switch 47 installed opposite to the rotor 45. An integrator 48 is provided to integrate the output voltage from 47. The reed switch 47 has one terminal connected to the power supply terminal and the other terminal grounded, and each time the magnet 46 in the rotor 45 passes through the reed switch 47 position as the rotor 45 rotates, Magnetically turned on.
An amplifier 49 is connected to the integrator 48, and the members 45-49 form a handling cylinder rotation speed detection circuit _C2 .
The rotation speed of the handling cylinder 13 is increased or decreased as the load on the handling cylinder 13 increases or decreases, and the handling cylinder rotation speed detection circuit _C2 outputs a voltage signal proportional to the rotation speed of the handling cylinder 13 at its output terminal. Output Vrev. In the first embodiment shown in FIG. 1-10, the opening degree of the dust feeding valve 15 is determined from the voltage signal Vloss from the grain loss detection circuit C ₁ and from the handling cylinder rotation speed detection circuit C ₂ . According to the voltage signal Vrev of
Since the operation of the threshing section 8 is controlled by adjusting the dust feeding valve 15, the dust feeding valve 15 will be specifically explained here. As shown in FIG. 5, a plurality of dust feeding valves 15 are provided on the top wall 12a of the handling chamber 12, each rotatably supported around a vertical pin 50. Each base end is pivotally connected by a vertical pin 52 to an interlocking plate 51 provided on the upper surface side of the top wall 12a. Therefore, when the interlocking plate 51 is moved forward and backward in the direction of the arrow shown in the figure, the dust feeding valve 15 is rotated around the vertical pin 50, and this rotational displacement causes the dust feeding valve 15 to move upward and downward from the top of the handling cylinder 13. By changing the relative angle to the arrangement direction of the handling teeth 14, which are arranged in a spiral manner, and appropriately narrowing, fully closing or fully opening the dust exhaust passage between the handling teeth 14, The rate of dust discharged from inside the handling room 12 is regulated as appropriate. The dust feeding valve 15, the specific structure of which has been explained above, is configured to change and adjust its opening degree by displacing the interlocking plate 51 using a dust feeding valve adjustment lever 53 shown in FIG. . As shown in FIG. 6, a single-acting hydraulic cylinder 54 for operating a lever is provided, the end of which is pivotally supported on the fuselage, and a piston rod 54 of this hydraulic cylinder 54 is provided.
a to the dust-feeding valve adjustment lever 53 as shown in the figure, and from the extended state of the hydraulic cylinder 54 in which the dust-feeding valve 15 assumes the standard opening position, the hydraulic oil is supplied to the oil chamber 54b of the hydraulic cylinder 54. The cylinder 54 is compressed by the supply, and the lever 53 is rotated in the direction of arrow A in FIG. 6, thereby closing the dust feeding valve 15. Re-opening to the standard opening degree after the dust feeding valve 15 is closed is performed by discharging hydraulic oil from the oil chamber 54b and extending the lever operating hydraulic cylinder 54 using the return spring 54c. As shown in FIG. 6, a hydraulic pump 57 is provided for supplying hydraulic oil at the hydraulic pressure set by the relief valve 56 from the oil tank 55 to the oil chamber 54b of the lever operating hydraulic cylinder 54. The hydraulic oil supply by the hydraulic pump 57 is selectively performed by an electromagnetic switching valve 58 between the pump 57 and the hydraulic cylinder 54. That is,
The electromagnetic switching valve 58 is normally operated under a spring bias at the neutral position N shown in the figure, that is, the neutral position N in which both the oil chamber 54b and the hydraulic pump 57 are connected to the hydraulic tank 55 and the hydraulic cylinder 54 is maintained in the extended position, and the solenoid 59 is energized, the hydraulic pump 57 is connected to the oil chamber 54b, and the hydraulic cylinder 54 is contracted. In the first embodiment shown in FIG. 1-10, the gear position of the transmission in the travel drive unit is also determined by the voltage signal from the aforementioned Glen loss detection circuit _C1 .
Vloss and voltage signal from handling cylinder rotation speed detection circuit C ₂
The vehicle speed of the combine harvester shown in the diagram is controlled by changing it according to Vrev.
Next, the configuration of the traveling drive section will be explained. The drive wheel 60 that drives the crawler 1 receives rotational drive from a drive section inside the mission case 61 shown in FIG.
It is constructed with a hydrostatic transmission 62 shown in FIG.
That is, as shown in FIG.
A variable displacement hydraulic pump 63 driven by
and a constant displacement hydraulic motor 64 which is interlocked and connected in the direction of the drive wheel 60, into a pair of oil supply and drainage circuits 65 and 66 that form a closed circuit together with the hydraulic pump 63 and the hydraulic motor 64. Then, connect
By changing and adjusting the angle of the swash plate 63a of the hydraulic pump 63 by operating the speed change lever 67, the oil discharge direction and discharge amount of the hydraulic pump 63 can be changed and controlled, and the rotation direction and rotation speed of the hydraulic motor 64 can be changed and controlled. A hydrostatic transmission 62 is provided that is configured to provide variable control. In FIG. 7, 68 is the oil supply and drain circuit 6.
High-pressure relief valves 2 and 63 set the oil pressure of the high-pressure side circuits; 69 and 70 are a pair of check valves 71 that allow only oil flow from the oil supply and discharge circuits 65 and 66 toward the high-pressure relief valve 68, respectively; 72 is a charge pump inserted into the oil supply circuit 71 and driven by the engine 11 to replenish the hydraulic oil; Oil supply circuit 7
Low pressure relief valve for setting the oil pressure of 1, 74, 75
are from the oil supply circuit 71 to the oil supply and discharge circuit 6, respectively.
These are a pair of check valves that allow oil flow paths only in the 5th and 66th directions. As shown in FIG. 8, a shift hydraulic cylinder 76 is provided with the end of the cylinder body pivotally supported on the machine body. It is designed to be connected to a shift lever 67 for operation so that the shift lever 67 can be rotationally displaced by the telescopic operation of the shift hydraulic cylinder 76. In order to selectively operate the hydraulic cylinders 76, an oil supply circuit 76 is provided which guides the hydraulic oil at the hydraulic pressure set by the relief valve 78 from the oil tank 55 by the hydraulic pump 77 toward the above-mentioned transmission hydraulic cylinders 76. An electromagnetic switching valve 82 as shown in the figure is provided between oil supply and drainage circuits 80 and 81 connected to the expansion oil chamber and the contraction oil chamber of the transmission hydraulic cylinder 76, respectively. This electromagnetic switching valve 82 connects the oil supply circuit 79 toward the oil tank 55, blocks both oil supply and discharge circuits 80 and 81, and has a neutral position N where the hydraulic cylinder 76 is stopped at a certain expansion/contraction position, and a solenoid The speed increasing position is moved by the excitation of 83, and the oil supply circuit 7
9 to the oil supply/discharge circuit 80, and the oil supply/discharge circuit 81 to the oil tank 55, the shift hydraulic cylinder 76 is extended, and the shift lever 67 is moved.
In the normal rotation direction of the hydraulic pump 63, its swash plate 63a
The speed increasing position is rotated in the direction of arrow A so that the angle is increased, and the decelerating position is moved by the excitation of the solenoid 84. The exhaust circuit 80 is connected to the oil tank 55, the shift hydraulic cylinder 76 is reduced, and the shift lever 67 is moved in the opposite direction of arrow A so that the angle of the swash plate 63a is decreased in the normal rotation direction of the hydraulic pump 63. 3 with the deceleration action position for rotationally displacing the
It has a position N,,. 8 in Figure 8
Reference numeral 5 denotes a lower limit speed regulating switch disposed within the rotation locus of the speed change lever 67, and this lower limit speed regulating switch 85 is connected to the ninth lower limit speed regulating switch 85 as will be described later.
It is incorporated in the control circuit shown in the figure, and the gear shift lever 67 controls the pump swash plate 63a and the hydraulic pump 6.
3. When rotationally displaced in the opposite direction of arrow A to a certain angle in the normal rotation direction, the lever 67 is turned off and the vehicle speed in the forward direction of the aircraft is restricted from falling below a certain speed. . Also the 8th
In the figure, 86 is an electromagnetic short-circuit valve that selectively short-circuits both the oil supply and discharge circuits 80 and 81 between the electromagnetic switching valve 82 and the shift hydraulic cylinder 76. Under spring bias, take the non-shorted position U shown and solenoid 87
is assumed to be moved to the short-circuit position S by the excitation of . When connected to solenoid 87, power supply 88
and a manual switch 89 are provided, and by turning on the manual switch 89, the electromagnetic short-circuit valve 86 is moved to the short-circuit position S. In the short-circuit position S of the electromagnetic short-circuit valve 86, the speed change lever 67 can be freely operated manually. Note that the solenoid 8 of the electromagnetic switching valve 82
3 and 84 may be configured to be excited and magnetized by a manual switch, and the angle of the swash plate 63a may be changed by the hydraulic cylinder 76 even during manual operation.
Of course it is possible. In the first embodiment shown in FIGS _. 1-10, the control circuit shown in _FIG .
By selectively energizing the solenoid 59 of the electromagnetic switching valve 58 shown in FIG. 6 and the solenoids 83 and 84 of the electromagnetic switching valve 82 shown in FIG. Vehicle speed control is performed by speed control and gear change of the hydrostatic transmission 62. Before explaining the configuration of the control circuit for this purpose, the control logic will be explained first.
As shown in Figure a, it is divided into two zones: an excessive loss zone Hg that is greater than a certain amount of loss and an underloss zone Lg that is less than the certain amount of loss.
The above constant loss amount is a voltage corresponding to the output voltage signal Vloss of the Glen loss detection circuit _C1 , and the first
As shown in Figure 0a, the loss reference voltage is Vdef. As shown in Figure 10b, the handling cylinder rotation speed is divided into a proper rotation speed zone M with a constant rotation speed range, an excessive rotation speed zone Hr with a higher rotation speed, and a rotation speed lower than the proper rotation speed zone M. It is divided into three zones including a low underspeed zone Lr, and the upper and lower limits of the appropriate rotation speed zone M are voltages corresponding to the output voltage signal Vrev of the handling cylinder rotation speed detection circuit _C2 , respectively. As shown in Figure 10b, the appropriate zone upper limit voltage Vomax and the appropriate zone lower limit voltage
It has become Vomin. And the control logic is
As shown in Table 1 below, there are six control areas,
, , , are assembled to control the opening degree of the dust feeding valve 15 and the vehicle speed control.

[Table] To explain the specific circuit configuration with reference to FIG. 9, first, a first comparator 90 is provided to which the output voltage signal Vloss of the Glenn loss detection circuit _C1 is supplied to the positive input terminal. The above-mentioned loss reference voltage Vdef is introduced into the negative input terminal of the first comparator 90 by adjusting the power supply voltage using a variable resistor 91.
Therefore, this first comparator 90 compares both voltages Vloss and Vdef and determines the voltage Vloss.
is larger than the voltage Vdef (Vloss>Vdef),
An excessive loss voltage signal Vgh is output in the excessive loss zone Hg shown in FIG. 10a. Further, a second comparator 92 that receives the output voltage signal Vrev of the handling cylinder rotation speed detection circuit C ₂ to the positive input terminal and a third comparator 93 that supplies the output voltage signal Vrev to the negative input terminal are provided. There is. Of these, the above-mentioned appropriate zone upper limit voltage Vomax is introduced into the negative input terminal of the second comparator 92 by adjusting the power supply voltage with a variable resistor 94. The above-mentioned appropriate zone lower limit voltage Vomin is introduced into the positive input terminal of the comparator 93 by further adjusting the power supply voltage by a variable resistor 95. Therefore, the second comparator 92 compares both voltages Vrev and Vomax led to its input terminal, and determines the voltage.
Vrev is larger than voltage Vomax (Vrev＞
The third comparator 93 outputs an excessive rotational voltage signal Vrh in the excessive rotational speed zone Hr shown in FIG. death,
Voltage Vrev is smaller than voltage Vomin (Vrev<
Vomin), the under-rotation voltage signal Vrl is output in the under-rotation speed zone Lr shown in FIG. 9b. Solenoid 5 of electromagnetic switching valve 58 shown in FIG.
9 and the solenoids 83 and 84 of the electromagnetic switching valve 82 shown in FIG.
It is incorporated as follows. That is, each of the solenoids 59, 83, 84 is connected in parallel with surge absorption diodes 96, 97, 98, and
One end is connected to the power supply terminal and the other end is grounded, and is incorporated into the control circuit. In the ground circuit of each solenoid 59, 83, 84, NPN transistors 99, 100, 10 whose emitters are grounded are included.
1 is inserted, and each transistor 99, 1
00,101 base pull down resistor 10
By grounding through 2,103,104,
A switching circuit is configured that is turned on by input signals to the bases of transistors 99, 100, and 101. Output voltage signals of comparators 90, 92, 93
Each of the above switching circuits or transistors 99, 100, 1 depending on the presence or absence of Vgh, Vrh, and Vrl.
In order to selectively turn on 01, the following circuit configuration is adopted. That is, as similarly shown in FIG. 9, an OR circuit 105 and first and second NAND circuits 106 and 107 are provided. Among these, to the input terminal of the OR circuit 105, a first comparator 90 is connected via an inverter 108, and a second comparator 92 and a third comparator 93 are each directly connected. In addition, a first comparator 90 is connected to the input terminal of the first NAND circuit 106.
9, and a second comparator 92 is directly connected. Furthermore, the second
The NAND circuit 107 includes a first comparator 9
0 and a second comparator 92 are each directly connected. In order to apply an input signal to the base of the transistor 99, a monomulti 110 whose output end is connected to the base is provided, and when a voltage signal is input, a rectangular voltage pulse is generated for t seconds.
At the input end of the monomulti 110 that outputs Pa,
OR circuit 105 and second NAND circuit 107,
It is connected via an inverter 111. From this, the monomulti 110 outputs an excessive loss voltage signal Vgh from the first comparator 90 and an excessive rotation voltage signal Vrh from the second comparator 92. When the second and third comparators 92 and 93 do not output voltage signals Vrh and Vrl while Vgh is being output, they operate to generate pulses.
Pa is output, thereby turning on the transistor 99 for t seconds. Also transistor 1
In order to apply an input signal to the base of 00, a pulse generator 1 whose output terminal is connected to the base is used.
12, and a NAND circuit 113 whose output terminal is connected to the input terminal of this pulse generator 112,
The output terminal of the first NAND circuit 106 is connected to the input terminal of this NAND circuit 113, and a monomultiplier outputs a rectangular voltage pulse Pb for t seconds when a voltage signal is input. The output terminal of 114 is connected. The input terminal of this monomulti 114 is connected to the output terminal of a NAND circuit 116, which is connected directly to the output terminal of the inverter 111 and to the output terminal of the monomulti 110 via an inverter 115. ,
It is connected via an inverter 117, and
The third comparator 93 is connected to the monomulti 114
Diode 11 that allows signal transmission only in the direction
It is connected via 8. As described above, the pulse generator 112 outputs the excessive rotation voltage signal Vrh while the first comparator 90 does not output the excessive loss voltage signal Vgh, and the output from the monomulti 114 operates to intermittently apply voltage pulses to the base of transistor 100 to
0 is turned on intermittently. Next, in order to apply an input signal to the base of the transistor 101, a pulse generator 119 is provided whose output terminal is connected to the base.
The output terminal of the inverter 117 is connected to the input terminal of the third comparator 93.
are connected via the diode 118.
As a result, the pulse generator 119 operates immediately when the third comparator 93 outputs the under-rotation voltage signal Vrl, regardless of whether the first comparator 90 outputs the excessive-loss voltage signal Vgh. , a voltage pulse is intermittently applied to the base of the transistor 101 to intermittently turn on the transistor 101, and the first comparator 9
0 is outputting the excessive rotation voltage signal voltage Vgh, the second comparator 92 outputs the excessive rotation voltage signal
When Vrh is output, both output voltage signals from the second comparator 92 and the third comparator 93
When Vrh and Vrl are no longer output and the excessive loss voltage signal Vgh is output from the first comparator 90, due to the existence of the monomulti 110, it operates after t seconds have elapsed and intermittently generates voltage pulses. It is applied to the base of the transistor 101 to turn on the transistor 101 intermittently. The selective ON operations of the transistors 99, 100, and 101 described above are summarized as shown in Table 2 below.

[Table] Transistor 99 turns on and solenoid 59
By energizing the solenoid 59 and energizing the solenoid 59, the electromagnetic switching valve 5 is activated as described above.
8 (FIG. 6) is displaced from the neutral position N to the operating position, and the dust feeding valve 15 is closed. When the transistor 100 turns on and the solenoid 83 is energized, the solenoid 83 is energized, thereby moving the electromagnetic switching valve 82 (FIG. 8) from the neutral position N to the speed increasing position. The transistor 101 is turned on and the solenoid 84 is energized, increasing the vehicle speed.
As described above, the electromagnetic switching valve 82 (FIG. 8) is changed from the neutral position N to the deceleration position, thereby reducing the vehicle speed. In addition, the excessive loss voltage signal Vgh column in Table 2 corresponds to the Glen loss column in Table 1, and
Over-rotation voltage signal Vrh column and under-rotation voltage signal in the table
The Vrl column corresponds to the handling cylinder rotation speed column in Table 1. Based on the above, the second control area in Table 1 is
It can be seen that the automatic control according to the logic listed in Table 1 can be achieved by the control circuit shown in FIG. 9, corresponding to each case in the table. In the above automatic control, the transistors 100 and 101 associated with the solenoids 83 and 84 of the electromagnetic switching valve 82 for increasing and decreasing the vehicle speed are intermittently turned on by output pulses from the pulse generators 112 and 119. Therefore, when the solenoids 83 and 84 are energized, the energization is performed intermittently. Therefore, the vehicle speed is increased or decreased intermittently or in stages, and problems such as the occurrence of a shock or excessive increase or deceleration due to a sudden change in vehicle speed are prevented. Further, the control circuit of FIG. 9 is provided with the above-mentioned monomulti 114, and the monomulti 114 is
Pulse generator 1 associated with transistor 100
Since it is connected to the NAND circuit 113 in the previous stage of 12 together with the second AND circuit 116, after the under-rotation voltage signal Vrl, which is a deceleration signal, is input from the third comparator 93 to the monomulti 114, the corresponding During a certain period of time t seconds during which the monomulti 114 operates, even if a signal for speed increase is input to the NAND circuit 113 from the second AND circuit 116 side, the NAND circuit 113 does not output a voltage signal. , therefore, the pulse generator 112 does not operate and no speed increase is performed. In this way, by not increasing the vehicle speed for a certain period of time after the vehicle speed has been decelerated, hunting is prevented and control is preferably performed in terms of work accuracy. The aforementioned lower limit speed regulation switch 85 (Fig. 8)
is inserted into the power supply circuit of the solenoid 84, as shown in FIG. Therefore, when this lower limit speed regulation switch 85 is turned off by the speed change lever 67 as described above, the solenoid 84 is not energized even if the pulse generator 119 is operating, and therefore, the electromagnetic switching valve 82 is not energized. As a result, the lower limit speed in the forward direction of the machine is regulated, and a decrease in work efficiency due to extreme deceleration is prevented. Similarly, as shown in FIG. 9, an NPN transistor 120 with a grounded emitter is connected to the output terminal of the second comparator 92, and the base of this transistor 120 is grounded via a pull-down resistor 121 to form a switching circuit. is configured. The output terminal of the third comparator 93 is connected to the base of the transistor 120. Therefore, the third comparator 93
As long as the second comparator 92 outputs the under-rotation voltage signal Vrl, even if the second comparator 92 unexpectedly outputs the over-rotation voltage signal Vrh for some reason, the over-rotation voltage signal Vrh will disappear due to grounding. That is, as is clear from the above, the third
The comparator 93 functions to compare the number of revolutions of the handling cylinder 13 with a set lower limit value and to energize the solenoid 84 for vehicle speed reduction based on the under-rotation voltage signal Vrl. As a result, priority is given to the deceleration side. The first embodiment shown in Fig. 1-10 is constructed as described above, and each part operates as described above, so that it can be easily used during harvesting operations. , it has the following advantages. That is, as is clear from Table 1, when the grain loss is low and the degree of sorting in the threshing section 8 is high, and the handling drum rotation speed is high and there is plenty of room in the threshing section 8, as in the control region, The vehicle speed is increased to improve work efficiency, and conversely, when the handling drum rotation speed is low and overload is applied to the threshing section 8, the vehicle speed is reduced to improve work efficiency, as shown in the control range. Accuracy is improved and overload removed.
In addition, as shown in the control region, when the grain loss is high and the degree of sorting in the threshing section 8 is poor without overload acting on the threshing section 8, the dust feeding valve 15 is first closed; As a result, the proportion of dust discharged from the handling chamber 12 of the threshing section 8 is maximized, and the degree of sorting, that is, the work accuracy is improved. In this way, if the grain loss is high and the sorting degree is not improved even after the above-mentioned t seconds, such as 5 to 10 seconds, by controlling the operation of the threshing section 8,
Operation control of the threshing section 8 is stopped by closing the dust feeding valve 15, and the vehicle speed is reduced, thereby improving work accuracy. In this way, in the control region, the operation of the threshing section 8 is first controlled by closing the dust feed valve 15, that is, the operation of the threshing section 8 is controlled so as not to reduce the work efficiency, and only when an appropriate working state cannot be obtained even then, the vehicle speed deceleration control is performed. By switching, control is achieved that increases work accuracy while maintaining work efficiency as high as possible. As described above, according to the first embodiment shown in Fig. 1-10, a harvesting operation in which both accuracy and efficiency are improved in a well-balanced manner is automatically achieved. be. Next, the second embodiment shown in FIG. 11 will be explained. In FIG. 11, 123 indicates the winnow shaft of the winnow 21,
The V-belt 12 is wound around the pulleys 125, 126 on both shafts 124, 123 from the drive shaft 124 on the side of the engine 11, which is parallel to the shaft 123.
It receives transmission through 7 and is rotated. In particular, the pulley 63 on the chisel shaft 123
Pulley half 1 on the fixed position side keyed on top
26a, and a movable pulley half 126b provided on the shaft 123 so as to be slidable but not relatively rotatable by means of a slide key 128, and both pulley half parts 126a, 126b.
The movable pulley half 126b is slid in the direction away from the stationary pulley half 126a by receiving both ends of the disk body 129 loosely fitted onto the winnowing shaft 123 and the movable pulley half 126b between them. A pair of compression springs 130 and 131 are provided. Furthermore, on the base end side of the movable pulley half 126b, a cylinder 132 is provided on the winnowing shaft 123, which is fixed to the machine frame and rotatably supports the winnowing shaft 123.
26b into the cylinder 1 in an oil-tight manner.
A single-acting hydraulic cylinder 133 having 32 as a cylinder body and a pulley half 126b as a piston, which is compressed by the compression springs 130 and 131 and extended by hydraulic action on an oil chamber 133a in the cylinder 132. A hydraulic cylinder 133 is configured. An oil distribution chamber 135 is formed at the tip of the winnowing shaft 123 by a seal housing 134 that rotatably supports the shaft 123.
is connected to the oil chamber 133a of the hydraulic cylinder 133 through an oil passage 136 bored in the winnowing shaft 123. Additionally, a pulley 125 on the drive shaft 124
Also, a fixed pulley half 125a is fixedly provided on the drive shaft 124, and a slide key 13 is mounted on the boss of the fixed pulley half 125a.
The movable pulley half 125b is mounted on the drive shaft 124 so as to be slidable but not relatively rotatable. A compression spring 1 whose both ends are received by the half portion 125b.
39, it is biased to slide in the direction of the stationary pulley half 125a. As a result of the above, the Karaoke shaft 123 changes from the state shown by the solid line in FIG.
Apply hydraulic pressure to a to move the movable pulley half 126a of the pulley 126 to the fixed pulley half 126.
a, as shown by the chain line, and pulley 12
6 Increase the effective diameter and adjust the V-belt 127 accordingly.
The movable pulley half 125b of the pulley 125 on the drive shaft 124 is connected to the fixed pulley half 1 through
When the pulley 125 is spaced apart from the pulley 25a as shown by the chain line and the effective diameter of the pulley 125 is made small, the pulley 125 is rotated at a low speed. Similarly, as shown in FIG. 11, in order to selectively apply hydraulic pressure to the above-mentioned hydraulic cylinder 133, a hydraulic circuit completely similar to the hydraulic circuit shown in FIG. 6 in the first embodiment is installed. Solenoid switching valve 5
The secondary side port of No. 8 is connected to the oil distribution chamber 135 described above, and the operation of the solenoid 59 of the electromagnetic switching valve 58 is controlled by a control circuit similar to that shown in FIG. It is assumed that From this point on, in the second embodiment shown in FIG.
In addition to controlling the vehicle speed, the rotational speed of the winnow 21 and, therefore, the wind force of the sorting air from the winnow 21 are controlled by controlling the position of the electromagnetic switching valve 58. This second
In the embodiment shown in FIG.
26,125 The effective diameter has been changed, and the karawino shaft 12
3. Therefore, the rotation speed of the winnower 21 is lowered, and the wind force of the sorting wind from the winnower 21 is weakened.
As a result, the operation of the threshing section 8 is controlled in a direction that reduces grain loss, and conversely, when the electromagnetic switching valve 58 is returned to the neutral position N, the effective diameter of the pulleys 126 and 125 increases in speed. The direction is changed, the number of revolutions of the winnowing machine 21 is increased, and the wind force of the sorting wind is increased again, thus,
The operation of the threshing section 8 is appropriately controlled. In the above embodiment, the load acting on the threshing section 8 was detected from the rotation speed of the handling drum 13. However, such a load applied to the threshing section 8 can also be detected from, for example, the number of rotations of the first conveyor 27 or the number of rotations of the second thrower 28 shown in FIG. Further, in the above embodiment, the grain detection loss detector 29 for detecting the proportion of lost grains in the waste from the threshing section 8 was provided as a sorting degree detector for detecting the degree of threshing sorting. 12 and 13 show a third embodiment in which, as such a sorting degree detector, a sorting degree detector 29A is provided which directly detects the sorting degree from the straw waste ratio in the sorted grains. is shown. That is, the threshing section 8 according to this third embodiment
Now, as shown in FIG. 12, the upper stroke rack 25 in the threshing section 8 shown in FIG. The No. 3 dust exhaust port 26, which is arranged in the upper rear direction and corresponds to the No. 3 dust exhaust port 26 shown in FIG. The dust exhaust port 143 is divided into an upper dust exhaust port 142 that discharges dust from the dust exhaust fan 141 and a lower dust exhaust port 143 that mainly discharges dust from the end of the stroke rack 20. The sorting degree detector 29A is a flow grain plate 144 provided below the grain sieve 19 and inclined in the direction of the first mouth 23, and is used to detect grains leaking through the grain sieve 19. It is provided on a flow board 144 that guides the grains toward the first port 23. The bandpass filter 30A attached to the selectivity detector 29A is different from the above-mentioned bandpass filter 30 in that, as shown in _{FIG .}
In the middle, only the voltage pulse P ₂ corresponding to straw waste is filtered, and the voltage pulse P ₁ corresponding to the grain is
The structure is designed to cut this and prevent it from being transmitted to the secondary side. From this, the selection degree detector 29A
The method directly detects the degree of sorting by detecting the proportion of straw waste in the grain after sorting. Therefore, the output signal of the bandpass filter 30A, together with the output signal from the threshing load detector side, is used in the same way as in the first and second embodiments to control the operation of the threshing section 8 and the vehicle speed of the combine. It is supposed to be possible to perform control. Note that if the selection degree is low when only one selection degree detector 29A is used, a plurality of detectors 29A may be provided, and the outputs thereof may be added together using an adder, and used for control purposes. Further, according to the present invention, when controlling the operation of the threshing section in addition to the vehicle speed control, the direct control target is the opening degree of the dust feeding valve 15 in the first embodiment, or the opening degree of the dust feeding valve 15 in the second embodiment. The present invention is not limited to one controlled object, such as the number of rotations of the winnowing machine 21, but it is also possible to directly control the operation of two or more controlled objects. FIG. 14 shows a fourth embodiment configured in this way.
The hydraulic circuit configuration is exactly the same as that shown in FIG. The diameter is adjusted at the same time. Furthermore, as described above, there are various types of controlled objects in the threshing section 8 that are directly controlled in addition to those described above.
That is, for example, the swinging sorting mechanism 17-20
The drive shaft rotation speed in the swing mechanism that swings the
Control is performed according to the detected threshing sorting degree and the load applied to the threshing section 8, and the swinging speed or frequency of the swinging sorting mechanism 17-20 is controlled so that the sorting degree is appropriate. A switching plate that can be rotated is provided at the grain flow branching point position between the first port 23 and the second port 24, and the posture of the switching plate can be changed to the maximum depending on the degree of threshing sorting and the threshing load. The operation of the threshing section 8 may be controlled by changing between the attitude of guiding grains to the opening 23 and the attitude of guiding the grain flow to the second opening 24 using a hydraulic cylinder or the like, or similarly, the operation of the threshing section 8 may be controlled. Direct objects to be controlled in the threshing section 8, such as the inclination angle, the rotation speed of the feed chain 9, or the inclination angle of the grain flow plate 144 (FIG. 12), are as follows:
You can choose from a variety of options. 15 and 16 show a specific example of such another controlled object. In the fifth embodiment shown in FIGS. 15 and 16, the swinging sorting mechanism 17-20
The chaff sheave 18 is configured to include a plurality of movable sheave plates 146A located on the front side and a plurality of fixed sheave plates 146B located on the rear side. That is, the fixed sheave plate 146B is the side plate 14 of the swinging sorting mechanism 17-20.
7, each movable sheave plate 146A has horizontal support shafts 148 protruding from both ends rotatably supported by the side plates 147. Horizontal support shaft 1 between
It is supported so as to be rotatable around 48. Then, the rotating arms 149 attached to the horizontal support shafts 148 at one side end are connected to the one side plate 14.
The pin 1 is attached to the interlocking plate 150 provided along the outer surface of the pin 7.
51 connection, the plurality of movable sheave plates 146A can be rotated at any time by moving the interlocking plate 150 back and forth. Interlocking plate 15
In order to move the 0 forward and backward, a hydraulic cylinder 152 is provided to the interlocking plate 150, and the end of a piston rod 152a is connected with a pin. In the illustrated case, the hydraulic cylinder 152 is configured as a single-acting type with a built-in spring 152b, and is extended by the supply of hydraulic pressure to move the movable sheave plate 146A into the small size shown in FIG. 16a. It is rotated from the inclination angle α ₁ to the large inclination angle α ₂ shown in FIG. 16b. The operation of this hydraulic cylinder 152 is controlled in the same manner as the hydraulic cylinder 54 shown in FIG. 6 and the hydraulic cylinder 133 shown in FIG. 11. Therefore, when the degree of threshing sorting in the threshing section 8 is poor,
As shown in FIG. 12b, the operation of the threshing section 8 is controlled so that the inclination angle of the movable sieve plate 146A is small, the rate of threshing leakage from the chaff sieve 18 is reduced, and the degree of sorting is improved. be done. As described above, the harvester of the present invention has a transmission 6
2, a reaping section 2-7 for reaping the planted grain culms, and a threshing section 8 for threshing and sorting the harvested grain culms, A sorting degree detector 29 or 29A for detecting the degree of threshing sorting in the threshing section 8;
A threshing load detector 44 is provided to detect the load acting on the threshing unit 8, and the operation of the threshing section 8 is controlled according to the output of the sorting degree detector 29 or 29A and the output of the threshing load detector 44. The device is configured to change and control the speed change by the machine 62 to obtain an appropriate working condition, and is configured to change and control the speed change by the machine 62 to obtain an appropriate working condition, depending on the maturity of the crop,
The operating condition of the self-propelled harvester, which is controlled by many factors such as length, lodging degree, moisture content, field condition, crop type, etc., is determined by the degree of degraining sorting, which is a direct indicator of work accuracy. , the load on the threshing section is the most accurate indicator for effortlessly maximizing work efficiency, and the threshing section, which mainly determines the accuracy of harvesting work, and the machine, which mainly determines the efficiency of harvesting work. Since the speed is controlled by the actual values of the above two indicators, two mutually contradictory factors, such as high harvest accuracy and high harvest efficiency in harvesting operations by self-propelled harvesters, can be achieved. It is designed to allow harvesting work to proceed while satisfying the demands as much as possible, and from this, even unskilled workers can control the work conditions themselves, which consumes their nerves. This allows you to work without fatigue.

[Brief explanation of the drawing]

FIG. 1 is a schematic side view of a combine harvester according to a first embodiment of the present invention, FIG. 2 is a schematic longitudinal side view of the main parts of the combine, FIG. 3 is a longitudinal side view of the main parts of the combine, and FIG. is a schematic diagram for explaining the action of the two members in the first embodiment, FIG. 5 is a perspective view showing a method of supporting the main parts of the combine, etc., and FIG. 6 is a schematic diagram for explaining the function of the two members in the first embodiment. A mechanical diagram and a hydraulic circuit diagram of the mechanism, FIG. 7 is a hydraulic circuit diagram showing the traveling transmission section of the combine harvester, and FIG. 8 shows a mechanism, hydraulic circuit, and electric circuit of the part related to the traveling transmission section. A mechanism diagram and a circuit diagram, FIG. 9 is a block diagram and an electric circuit diagram showing the electric control circuit in the first embodiment, and FIGS. 10 a and b are explanations showing the control range setting in the first embodiment, respectively. 11 is a vertical sectional view and hydraulic circuit diagram showing the main parts of a second embodiment of the invention, and FIG. 12 is a schematic vertical sectional side view of the main parts of a combine according to the third embodiment of the invention. FIG. 13 is a schematic diagram for explaining the action of the two members in the third embodiment, FIG. 14 is a longitudinal sectional view and hydraulic circuit diagram of the main parts of a combine according to the fourth embodiment of the present invention, and FIG. The figure is a perspective view of the main parts of a combine according to a fifth embodiment of the present invention.
FIG. 6 is a longitudinal sectional side view for explaining an operation of the fifth embodiment. 1... Crawler, 4... Cutting blade, 8... Threshing section, 11...
Engine, 13... Handling cylinder, 13a... Handling cylinder shaft, 15...
Dust feeding valve, 18... Chaff sieve, 21... Karasaki, 22
...dust exhaust fan, 23...first port, 26...third dust exhaust port, 29...grain loss detector, 32...hinge plate,
Horizontal pin, 38... tension spring, 41... monomulti,
42... Integrator, 44... Handling cylinder rotation speed detector, 45...
Rotor, 46...Magnet, 47...Reed switch, 48...Integrator, _C1 ...Glenn loss detection circuit,
C ₂ ... Handling cylinder rotation speed detection circuit, 50... Vertical pin, 5
DESCRIPTION OF SYMBOLS 1... Interlocking plate, 52... Vertical pin, 53... Dust feed valve adjustment lever, 54... Hydraulic cylinder for lever operation, 58
...Solenoid switching valve, 59...Solenoid, 61...Mission case, 62...Hydrostatic transmission, 63...Hydraulic pump, 63a...Swash plate, 64...Hydraulic motor, 65, 66...Oil supply/drain circuit, 67 ... Gear shift lever, 76... Hydraulic cylinder for gear change, 82... Solenoid switching valve, 83, 84... Solenoid, 85... Lower limit speed regulation switch, 86... Solenoid short circuit valve, 90, 92, 93... Comparator, 99,
100, 101...transistor, 102, 10
3,104...Pull-down resistor, 105...OR circuit, 106,107...NAND circuit, 108,1
09...Inverter, 110...Mono multi, 112
...Pulse generator, 113...NAND circuit, 114
...Mono multi, 115...Inverter, 116...
NAND circuit, 117... Inverter, 118... Diode, 119... Pulse generator, 123... Karaoke shaft, 124... Drive shaft, 125, 126... Pulley, 125a, 126a... Fixed side pulley half,
125b, 126b...Movable pulley half, 12
7... V belt, 130, 131... Compression spring, 13
2...Cylinder, 133...Hydraulic cylinder, 135...
Oil distribution chamber, 136...oil passage, 139...compression spring, 2
9A... Sorting degree detector, 30A... Band pass filter, 144... Grain flow plate, 146A... Movable sieve plate,
146B...Fixed sheave plate, 148...Horizontal support shaft, 1
49... Rotating arm, 150... Interlocking plate, 151... Pin, 152... Hydraulic cylinder.

Claims (1)

[Scope of Claims] 1. A self-propelled harvester equipped with a traveling drive unit having a transmission, a reaping unit that reaps planted grain culms, and a threshing unit that threshes and sorts the harvested grain culms. A sorting degree detector for detecting the degree of threshing sorting in the threshing section and a threshing load detector for detecting the load acting on the threshing section are provided, and the output of the sorting degree detector and the threshing load detector are provided. According to the output, the operation of the threshing section is controlled, and the speed change by the transmission is controlled to change the speed, so as to obtain an appropriate working state.
A self-propelled harvester characterized by the following configurations. 2. It is characterized in that the operation control of the threshing section is given priority over the speed change control, and the speed change control is performed only when an appropriate working condition cannot be obtained by the operation control of the threshing section. A self-propelled harvesting machine according to claim 1.