CN108835092B - High-clearance sprayer spray rod suspension control hydraulic system - Google Patents
High-clearance sprayer spray rod suspension control hydraulic system Download PDFInfo
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- CN108835092B CN108835092B CN201810816802.8A CN201810816802A CN108835092B CN 108835092 B CN108835092 B CN 108835092B CN 201810816802 A CN201810816802 A CN 201810816802A CN 108835092 B CN108835092 B CN 108835092B
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- A—HUMAN NECESSITIES
- A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
- A01M—CATCHING, TRAPPING OR SCARING OF ANIMALS; APPARATUS FOR THE DESTRUCTION OF NOXIOUS ANIMALS OR NOXIOUS PLANTS
- A01M7/00—Special adaptations or arrangements of liquid-spraying apparatus for purposes covered by this subclass
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- A—HUMAN NECESSITIES
- A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
- A01M—CATCHING, TRAPPING OR SCARING OF ANIMALS; APPARATUS FOR THE DESTRUCTION OF NOXIOUS ANIMALS OR NOXIOUS PLANTS
- A01M7/00—Special adaptations or arrangements of liquid-spraying apparatus for purposes covered by this subclass
- A01M7/005—Special arrangements or adaptations of the spraying or distributing parts, e.g. adaptations or mounting of the spray booms, mounting of the nozzles, protection shields
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- A—HUMAN NECESSITIES
- A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
- A01M—CATCHING, TRAPPING OR SCARING OF ANIMALS; APPARATUS FOR THE DESTRUCTION OF NOXIOUS ANIMALS OR NOXIOUS PLANTS
- A01M7/00—Special adaptations or arrangements of liquid-spraying apparatus for purposes covered by this subclass
- A01M7/0089—Regulating or controlling systems
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Abstract
The invention relates to a spray rod control hydraulic system of a high-clearance spraying machine. According to the invention, the hydraulic unit is controlled by the vertical active and passive suspensions, and the defects of the passive suspensions can be made up by controlling the posture of the spray rod, so that the spray rod can swing along with the low-frequency vehicle body well, and the ground clearance of the spray rod or the crop is ensured to be unchanged; by the dynamic pressure feedback unit, the dynamic characteristic of the hydraulic system can be improved by generating load damping in direct proportion to the change of the load pressure under the condition of not changing the steady-state characteristic of the system, the pressure impact is effectively absorbed, the load pressure oscillation of the system is filtered, the vibration of the spray rod is attenuated, and the spraying quality is improved; through the load feedback loop, the flow of hydraulic oil output to the execution element can be adjusted according to the change of the actual load in the working process of the system, the control precision of the system is improved, and the energy loss of the system is reduced; the problems of spray rod collision damage, breakage and the like when the spray rod encounters a barrier in the field operation process can be effectively prevented through the anti-collision device.
Description
Technical Field
The invention relates to a hydraulic system, in particular to a spray rod control hydraulic system of a high-clearance spraying machine, which can realize the functions of switching between a driving suspension and a driven suspension of a spray rod of the high-clearance spraying machine, adjusting the height of the spray rod, folding and preventing collision.
Background
The high-clearance boom sprayer is a large-scale high-end plant protection agricultural machine, has the characteristics of wide application range, high working efficiency, uniform spraying, reasonable dosage application, low pesticide application cost and the like, and is widely applied to field operation. Along with the improvement of the requirements of people on the operation speed, the operation precision and the economic environmental protection performance of a large-scale spraying machine, higher requirements are also provided for the response speed, the working stability and the energy conservation performance of a boom suspension hydraulic system, but the improvement of the dynamic performance of the hydraulic system is often contradictory to the maintenance of higher stability of the system, especially for a large-span, low-rigidity and weak-damping flexible boom, the underdamped boom suspension hydraulic system is difficult to effectively absorb pressure impact and filter system load pressure oscillation, so that the residual vibration after the attitude adjustment of the flexible boom is difficult to automatically attenuate, the stability and the spraying precision during the attitude adjustment of the boom are reduced, and the service life of the boom is also shortened. Most of the existing boom suspension control hydraulic systems are passive balance adjustment systems, so that the influence of vehicle body swing and terrain change on spraying quality cannot be actively reduced, and the operation quality and pesticide application efficiency of the high-clearance spraying machine are influenced.
Disclosure of Invention
In view of the above technical problems, an object of the present invention is to provide a hydraulic system for controlling a boom suspension of a spraying machine based on load feedback and dynamic pressure feedback principles, which can reduce energy consumption of the system, absorb pressure shock, filter load pressure oscillation of the system, and increase stability of the system on the basis of realizing basic functions (active and passive suspension switching, boom height adjustment, folding, and collision avoidance) of the boom suspension.
In order to achieve the purpose, the invention provides the following technical scheme:
the invention provides a spray rod suspension control hydraulic system of a high-clearance spraying machine, which comprises a differential pressure type overflow valve 1, a hydraulic pump 38, a lifting hydraulic unit, a left spray rod folding profiling hydraulic unit, a right spray rod folding profiling hydraulic unit and a vertical active and passive suspension control hydraulic unit;
the lifting hydraulic unit comprises a first fixed differential pressure reducing valve 2, a first two-position three-way proportional reversing valve 3, a first two-position two-way proportional reversing valve 4, a first throttle hole 5, a first sensing one-way valve 6, a first lifting hydraulic cylinder 9 and a second lifting hydraulic cylinder 10;
an oil outlet of the first fixed differential pressure reducing valve 2 is connected with an oil inlet of a first two-position three-way proportional reversing valve 3; the oil outlet of the first two-position three-way proportional reversing valve 3 is respectively connected with a rodless cavity of the first lifting hydraulic cylinder 9 and a rodless cavity of the second lifting hydraulic cylinder 10; an oil inlet of the first throttling hole 5 is connected with a feedback oil port of the first fixed differential pressure reducing valve 2, and an oil outlet of the first throttling hole 5 is connected with an oil inlet of the first two-position two-way proportional reversing valve 4; the oil outlet of the first two-position two-way proportional reversing valve 4 is respectively connected with a rodless cavity of the first lifting hydraulic cylinder 9 and a rodless cavity of the second lifting hydraulic cylinder 10; an oil inlet of the first sensing check valve 6 is respectively connected with a feedback oil port of the first fixed differential pressure reducing valve 2 and a feedback oil port of the first two-position three-way proportional reversing valve 3, and an oil outlet of the first sensing check valve 6 is connected with a control oil port of the differential pressure overflow valve 1;
the left spray rod folding profiling hydraulic unit and the right spray rod folding profiling hydraulic unit are provided with the same component composition and a connecting loop, and both comprise a profiling unit, a folding unit and an extending unit;
the profiling unit comprises a second constant-differential pressure reducing valve 11, a second two-position three-way proportional reversing valve 12, a second two-position two-way proportional reversing valve 13, a second orifice 14, a second sensing one-way valve 15 and a profiling hydraulic cylinder 18;
an oil outlet of the second constant-differential pressure reducing valve 11 is connected with an oil inlet of a second two-position three-way proportional reversing valve 12, and an oil outlet of the second two-position three-way proportional reversing valve 12 is connected with a rod cavity of the profiling hydraulic cylinder 18; an oil inlet of the second throttle hole 14 is connected with a feedback oil port of the second constant-differential pressure reducing valve 11, and an oil outlet of the second throttle hole 14 is connected with an oil inlet of the second two-position two-way proportional reversing valve 13; the oil outlet of the second two-position two-way proportional reversing valve 13 is connected with a rod cavity of the profiling hydraulic cylinder 18; an oil inlet of the second sensing check valve 15 is respectively connected with a feedback oil port of the second constant-differential pressure reducing valve 11 and a feedback oil port of the second two-position three-way proportional reversing valve 12, and an oil outlet of the second sensing check valve 15 is connected with a control oil port of the differential pressure overflow valve 1;
the folding unit comprises a third sensing one-way valve 25, a first throttle valve 19, a first three-position five-way reversing valve 20 and a folding hydraulic cylinder 24;
an oil outlet of the first throttle valve 19 is connected with an oil inlet of a first three-position five-way reversing valve 20, and two oil outlets of the first three-position five-way reversing valve 20 are respectively connected with a rod cavity and a rodless cavity of a folding hydraulic cylinder 24; an oil inlet of the third sensing check valve 25 is connected with a sensing oil port of the first three-position five-way reversing valve 20, and an oil outlet of the third sensing check valve 25 is connected with a control oil port of the differential pressure type overflow valve 1;
the extension unit comprises a fourth sensing one-way valve 26, a second throttle valve 27, a second three-position five-way reversing valve 28, a first one-way throttle valve 29 and an extension hydraulic cylinder 30;
the oil outlet of the second throttle valve 27 is connected with the oil inlet of a second three-position five-way reversing valve 28, two oil outlets of the second three-position five-way reversing valve 28 are respectively connected with the oil inlet of a first one-way throttle valve 29, and the oil outlets of the two first one-way throttle valves 29 are respectively connected with a rod cavity and a rodless cavity of an extension hydraulic cylinder 30; an oil inlet of the fourth sensing check valve 26 is connected with a sensing oil port of the second three-position five-way reversing valve 28, and an oil outlet of the fourth sensing check valve is connected with a control oil port of the differential pressure type overflow valve 1;
the vertical active and passive suspension control hydraulic unit comprises a third constant-differential pressure reducing valve 31, a fifth sensing one-way valve 32, a three-position five-way proportional reversing valve 33, a two-position two-way electromagnetic valve 34, a second one-way throttle valve 35, a first active balancing hydraulic cylinder 36 and a second active balancing hydraulic cylinder 37;
an oil outlet of the third constant-differential-pressure reducing valve 31 is connected with an oil inlet of a three-position five-way proportional reversing valve 33, two oil outlets of the three-position five-way proportional reversing valve 33 are respectively connected with an oil inlet of one two-position two-way electromagnetic valve 34, oil outlets of the two-position two-way electromagnetic valves 34 are respectively connected with an oil inlet of one second one-way throttle valve 35, and oil outlets of the two second one-way throttle valves 35 are respectively connected with a rodless cavity of a first active balancing hydraulic cylinder 36 and a rodless cavity of a second active balancing hydraulic cylinder 37; an oil inlet of the fifth sensing check valve 32 is connected with a feedback oil port of the third constant-differential-pressure relief valve 31, and an oil outlet of the fifth sensing check valve 32 is connected with a control oil port of the differential-pressure overflow valve 1;
an oil inlet of the hydraulic pump 38 is connected with a hydraulic oil tank 41 through an oil outlet filter 40, and an oil outlet of the hydraulic pump 38 is respectively connected with an oil inlet of the differential pressure type overflow valve 1, an oil inlet of the first differential pressure reduction valve 2, an oil inlet of the second differential pressure reduction valve 11, an oil inlet of the first throttle valve 19, an oil inlet of the second throttle valve 27 and an oil inlet of the third differential pressure reduction valve 31;
the oil return port of the differential pressure type overflow valve 1, the oil return port of the first two-position two-way proportional reversing valve 4, the oil return port of the second two-position two-way proportional reversing valve 13, the oil return port of the first three-position five-way reversing valve 20, the oil return port of the second three-position five-way reversing valve 28 and the oil return port of the three-position five-way proportional reversing valve 33 are all connected with a hydraulic oil tank 41 through an oil return filter 39;
the differential pressure type overflow valve 1, a first sensing one-way valve 6 of the lifting hydraulic unit, a second sensing one-way valve 15, a third sensing one-way valve 25, a fourth sensing one-way valve 26 of the left spray rod folding profiling hydraulic unit and the right spray rod folding profiling hydraulic unit, and a fifth sensing one-way valve 32 of the vertical active and passive suspension control hydraulic unit jointly form a load feedback loop.
The boom suspension control hydraulic system of the high-ground-clearance spraying machine further comprises a front anti-collision valve 21, a front anti-collision hydraulic cylinder 23 and a pair of rear anti-collision valves 22;
the two rear anti-collision valves 22 are respectively arranged on oil paths of two oil outlets of a first three-position five-way reversing valve 20 and a rod cavity and a rodless cavity of the folding hydraulic cylinder 24 in a folding unit of the left spray rod folding profiling hydraulic unit and a folding unit of the right spray rod folding profiling hydraulic unit, wherein the two oil outlets of the first three-position five-way reversing valve 20 are respectively connected with an oil inlet and an oil return port of the rear anti-collision valve 22, and the two oil outlets of the rear anti-collision valve 22 are respectively connected with the rod cavity and the rodless cavity of the folding hydraulic cylinder 24;
an oil inlet of the front anti-collision valve 21 is connected with an oil outlet of a first three-position five-way reversing valve 20 in a folding unit of the left spray rod folding profiling hydraulic unit or a folding unit of the right spray rod folding profiling hydraulic unit, and an oil outlet of the front anti-collision valve 21 is connected with a rodless cavity of a front anti-collision hydraulic cylinder 23.
The oil circuit between the first lifting hydraulic cylinder 9 and the first two-position three-way proportional reversing valve 3 is provided with a first dynamic pressure feedback unit, the first dynamic pressure feedback unit comprises a first damping throttle valve 7 and a lifting energy accumulator 8, an oil inlet of the first damping throttle valve 7 is connected to the oil circuit between the first lifting hydraulic cylinder 9 and the first two-position three-way proportional reversing valve 3, and an oil outlet of the first damping throttle valve 7 is connected with the lifting energy accumulator 8.
And a second dynamic pressure feedback unit is arranged on an oil path between the profiling hydraulic cylinder 18 and the second two-position three-way proportional reversing valve 12, the second dynamic pressure feedback unit comprises a second damping throttle valve 16 and a profiling energy accumulator 17, an oil inlet of the second damping throttle valve 16 is connected to the oil path between the profiling hydraulic cylinder 18 and the second two-position three-way proportional reversing valve 12, and an oil outlet of the second damping throttle valve is connected with the profiling energy accumulator 17.
A safety valve 42 is arranged on the load feedback loop, and an oil return port of the safety valve 42 is connected to an oil return path of an oil return port of the differential pressure type overflow valve 1.
Compared with the prior art, the invention has the beneficial effects that:
1. through the vertical active and passive suspension control hydraulic unit consisting of the third constant-differential pressure reducing valve 31, the fifth sensing one-way valve 32, the three-position five-way proportional reversing valve 33, the two-position two-way electromagnetic valve 34, the second one-way throttle valve 35, the first active balancing hydraulic cylinder 36 and the second active balancing hydraulic cylinder 37, the defect of a passive suspension can be overcome by controlling the posture of the spray rod, so that the spray rod can better swing along with a low-frequency vehicle body, and the gap of the spray rod from the ground or crops is ensured to be unchanged.
2. Through the dynamic pressure feedback unit consisting of the adjustable first damping throttle valve 7, the lifting energy accumulator 8, the adjustable second damping throttle valve 16 and the profiling energy accumulator 17, the dynamic characteristic of the hydraulic system can be improved by generating load damping in proportion to the change of the load pressure under the condition of not changing the steady-state characteristic of the system, the pressure impact is effectively absorbed, the load pressure oscillation of the system is filtered, the vibration of the spray rod is attenuated, and the spraying quality is improved.
3. Through a load feedback loop consisting of the differential pressure type overflow valve 1, the first sensing check valve 6, the second sensing check valve 15, the third sensing check valve 25, the fourth sensing check valve 26 and the fifth sensing check valve 32, the flow of hydraulic oil output to an execution element can be adjusted according to the change of the actual load in the working process of the system, the control precision of the system is improved, and the energy loss of the system is reduced.
4. The anti-collision device consisting of the safety valve 42, the front anti-collision valve 21, the rear anti-collision valve 22, the anti-collision hydraulic cylinder 23 and the profiling hydraulic cylinder 24 can effectively prevent the problems of collision damage, breakage and the like of the spray rod when the spray rod encounters an obstacle in the field operation process.
Drawings
Fig. 1 is a schematic diagram of a boom suspension control hydraulic system of the high-clearance spraying machine.
Wherein the reference numerals are:
1 differential pressure type overflow valve 2 first constant differential pressure reducing valve
3 first two-position three-way proportional reversing valve 4 first two-position two-way proportional reversing valve
5 first orifice 6 first sensing check valve
7 first damping throttle valve 8 lifting accumulator
9 first lifting hydraulic cylinder 10 second lifting hydraulic cylinder
11 second constant-differential pressure-reducing valve 12 second two-position three-way proportional reversing valve
13 second two-position two-way proportional reversing valve 14 second orifice
15 second sensing check valve 16 second damping throttle valve
17 copying energy accumulator 18 copying hydraulic cylinder
19 first throttle valve 20 first three-position five-way change valve
21 front anti-collision valve and 22 rear anti-collision valve
23 front anti-collision hydraulic cylinder 24 folding hydraulic cylinder
25 third sensing check valve 26 fourth sensing check valve
27 second throttle valve 28 second three-position five-way change valve
29 first one-way throttle 30 extension hydraulic cylinder
31 third constant-pressure-difference pressure-reducing valve 32 fifth sensing check valve
33 three-position five-way proportional reversing valve 34 two-position two-way electromagnetic valve
35 second one-way throttle valve 36 first active balancing hydraulic cylinder
37 second active balance hydraulic cylinder 38 hydraulic pump
39 return oil filter 40 outlet oil filter
41 hydraulic oil tank 42 safety valve
Detailed Description
The invention is further illustrated with reference to the following figures and examples.
As shown in figure 1, the hydraulic control system for the spray rod suspension of the high-clearance spraying machine comprises a differential pressure type overflow valve 1, a hydraulic pump 38, a lifting hydraulic unit, a left spray rod folding profiling hydraulic unit, a right spray rod folding profiling hydraulic unit and a vertical active and passive suspension control hydraulic unit.
The lifting hydraulic unit comprises a first fixed-differential pressure reducing valve 2, a first two-position three-way proportional directional valve 3, a first two-position two-way proportional directional valve 4, a first throttle hole 5, a first sensing one-way valve 6, a first lifting hydraulic cylinder 9 and a second lifting hydraulic cylinder 10.
An oil outlet of the first fixed differential pressure reducing valve 2 is connected with an oil inlet of a first two-position three-way proportional reversing valve 3; the oil outlet of the first two-position three-way proportional reversing valve 3 is respectively connected with the rodless cavity of the first lifting hydraulic cylinder 9 and the rodless cavity of the second lifting hydraulic cylinder 10. An oil inlet of the first throttling hole 5 is connected with a feedback oil port of the first fixed differential pressure reducing valve 2, and an oil outlet of the first throttling hole 5 is connected with an oil inlet of the first two-position two-way proportional reversing valve 4; the oil outlet of the first two-position two-way proportional reversing valve 4 is respectively connected with the rodless cavity of the first lifting hydraulic cylinder 9 and the rodless cavity of the second lifting hydraulic cylinder 10. An oil inlet of the first sensing check valve 6 is respectively connected with a feedback oil port of the first fixed differential pressure reducing valve 2 and a feedback oil port of the first two-position three-way proportional reversing valve 3, and an oil outlet of the first sensing check valve 6 is connected with a control oil port of the differential pressure type overflow valve 1.
Preferably, a first dynamic pressure feedback unit is arranged on an oil path between the first lifting hydraulic cylinder 9 and the first two-position three-way proportional directional valve 3, the first dynamic pressure feedback unit comprises a first damping throttle valve 7 and a lifting energy accumulator 8, an oil inlet of the first damping throttle valve 7 is connected to the oil path between the first lifting hydraulic cylinder 9 and the first two-position three-way proportional directional valve 3, and an oil outlet of the first damping throttle valve 7 is connected with the lifting energy accumulator 8.
The left spray rod folding profiling hydraulic unit and the right spray rod folding profiling hydraulic unit are provided with the same component and a connecting loop, and both comprise profiling units, folding units and extending units.
The profiling unit comprises a second constant-differential pressure reducing valve 11, a second two-position three-way proportional reversing valve 12, a second two-position two-way proportional reversing valve 13, a second throttling hole 14, a second sensing one-way valve 15 and a profiling hydraulic cylinder 18.
An oil outlet of the second constant-differential pressure reducing valve 11 is connected with an oil inlet of a second two-position three-way proportional reversing valve 12, and an oil outlet of the second two-position three-way proportional reversing valve 12 is connected with a rod cavity of the profiling hydraulic cylinder 18; an oil inlet of the second throttle hole 14 is connected with a feedback oil port of the second constant-differential pressure reducing valve 11, and an oil outlet of the second throttle hole 14 is connected with an oil inlet of the second two-position two-way proportional reversing valve 13; the oil outlet of the second two-position two-way proportional reversing valve 13 is connected with a rod cavity of the profiling hydraulic cylinder 18; an oil inlet of the second sensing check valve 15 is respectively connected with a feedback oil port of the second constant-differential pressure reducing valve 11 and a feedback oil port of the second two-position three-way proportional reversing valve 12, and an oil outlet of the second sensing check valve 15 is connected with a control oil port of the differential pressure overflow valve 1.
Preferably, a second dynamic pressure feedback unit is arranged on an oil path between the profiling hydraulic cylinder 18 and the second two-position three-way proportional reversing valve 12, the second dynamic pressure feedback unit comprises a second damping throttle valve 16 and a profiling energy accumulator 17, an oil inlet of the second damping throttle valve 16 is connected to the oil path between the profiling hydraulic cylinder 18 and the second two-position three-way proportional reversing valve 12, and an oil outlet of the second damping throttle valve is connected with the profiling energy accumulator 17.
The folding unit comprises a third sensing check valve 25, a first throttle valve 19, a first three-position five-way directional valve 20 and a folding hydraulic cylinder 24.
An oil outlet of the first throttle valve 19 is connected with an oil inlet of a first three-position five-way reversing valve 20, and two oil outlets of the first three-position five-way reversing valve 20 are respectively connected with a rod cavity and a rodless cavity of a folding hydraulic cylinder 24. An oil inlet of the third sensing check valve 25 is connected with a sensing oil port of the first three-position five-way reversing valve 20, and an oil outlet of the third sensing check valve 25 is connected with a control oil port of the differential pressure type overflow valve 1.
Preferably, the boom suspension control hydraulic system of the high-ground-clearance spraying machine further comprises a front anti-collision valve 21, a rear anti-collision valve 22 and a front anti-collision hydraulic cylinder 23. The two rear anti-collision valves 22 are respectively arranged on oil paths of two oil outlets of a first three-position five-way reversing valve 20 and a rod cavity and a rodless cavity of the folding hydraulic cylinder 24 in a folding unit of the left spray rod folding profiling hydraulic unit and a folding unit of the right spray rod folding profiling hydraulic unit, wherein the two oil outlets of the first three-position five-way reversing valve 20 are respectively connected with an oil inlet and an oil return port of the rear anti-collision valve 22, and the two oil outlets of the rear anti-collision valve 22 are respectively connected with the rod cavity and the rodless cavity of the folding hydraulic cylinder 24; an oil inlet of the front anti-collision valve 21 is connected with an oil outlet of a first three-position five-way reversing valve 20 in a folding unit of the left spray rod folding profiling hydraulic unit or a folding unit of the right spray rod folding profiling hydraulic unit, and an oil outlet of the front anti-collision valve 21 is connected with a rodless cavity of a front anti-collision hydraulic cylinder 23.
The extension unit comprises a fourth sensing check valve 26, a second throttle valve 27, a second three-position five-way reversing valve 28, a first check throttle valve 29 and an extension hydraulic cylinder 30.
The oil outlet of the second throttle valve 27 is connected with the oil inlet of a second three-position five-way reversing valve 28, two oil outlets of the second three-position five-way reversing valve 28 are respectively connected with the oil inlet of a first one-way throttle valve 29, and the oil outlets of the two first one-way throttle valves 29 are respectively connected with a rod cavity and a rodless cavity of an extension hydraulic cylinder 30; an oil inlet of the fourth sensing check valve 26 is connected with a sensing oil port of the second three-position five-way reversing valve 28, and an oil outlet of the fourth sensing check valve is connected with a control oil port of the differential pressure type overflow valve 1.
The vertical active and passive suspension control hydraulic unit comprises a third constant-differential pressure reducing valve 31, a fifth sensing one-way valve 32, a three-position five-way proportional reversing valve 33, a two-position two-way electromagnetic valve 34, a second one-way throttle valve 35, a first active balancing hydraulic cylinder 36 and a second active balancing hydraulic cylinder 37.
The oil outlet of the third constant-differential-pressure reducing valve 31 is connected with the oil inlet of a three-position five-way proportional reversing valve 33, two oil outlets of the three-position five-way proportional reversing valve 33 are respectively connected with the oil inlet of a two-position two-way electromagnetic valve 34, the oil outlets of the two-position two-way electromagnetic valves 34 are respectively connected with the oil inlet of a second one-way throttle valve 35, and the oil outlets of the two second one-way throttle valves 35 are respectively connected with a rodless cavity of a first active balancing hydraulic cylinder 36 and a rodless cavity of a second active balancing hydraulic cylinder 37. An oil inlet of the fifth sensing check valve 32 is connected with a feedback oil port of the third constant-differential-pressure relief valve 31, and an oil outlet of the fifth sensing check valve 32 is connected with a control oil port of the differential-pressure overflow valve 1.
An oil inlet of the hydraulic pump 38 is connected with a hydraulic oil tank 41 through an oil filter 40, and an oil outlet of the hydraulic pump 38 is respectively connected with an oil inlet of the differential pressure type overflow valve 1, an oil inlet of the first differential pressure reducing valve 2, an oil inlet of the second differential pressure reducing valve 11, an oil inlet of the first throttle valve 19, an oil inlet of the second throttle valve 27 and an oil inlet of the third differential pressure reducing valve 31.
The oil return port of the differential pressure type overflow valve 1, the oil return port of the first two-position two-way proportional reversing valve 4, the oil return port of the second two-position two-way proportional reversing valve 13, the oil return port of the first three-position five-way reversing valve 20, the oil return port of the second three-position five-way reversing valve 28 and the oil return port of the three-position five-way proportional reversing valve 33 are all connected with a hydraulic oil tank 41 through an oil return filter 39.
The differential pressure type overflow valve 1, a first sensing one-way valve 6 of the lifting hydraulic unit, a second sensing one-way valve 15, a third sensing one-way valve 25, a fourth sensing one-way valve 26 of the left spray rod folding profiling hydraulic unit and the right spray rod folding profiling hydraulic unit, and a fifth sensing one-way valve 32 of the vertical active and passive suspension control hydraulic unit jointly form a load feedback loop.
A safety valve 42 is arranged on the load feedback loop, and an oil return port of the safety valve 42 is connected to an oil return path of an oil return port of the differential pressure type overflow valve 1.
The working process of the invention is as follows:
(1) vertical active and passive suspension control system. When the two-position two-way electromagnetic valves 34 are powered off, and the valve core is in a closed position, oil is cut off, the first active balance hydraulic cylinder 36 and the second active balance hydraulic cylinder 37 are locked, at the moment, the spray rod cannot be leveled under the action of the gravity of the spray rod, and the passive suspension is in a closed state; when the two-position two-way electromagnetic valves 34 are electrified and opened, the three-position five-way proportional reversing valve 33 is in a middle position, piston rods of the first active balance hydraulic cylinder 36 and the second active balance hydraulic cylinder 37 extend out or retract under the action of the gravity of the spray rod, oil in the oil cylinder flows through the second one-way throttle valve 35 with adjustable opening degree to generate different damp for adjusting the movement speed of the oil cylinder, and at the moment, the spray rod suspension is in a passive balance adjusting state; when the two-position two-way electromagnetic valves 34 and the three-position five-way proportional reversing valve 33 are simultaneously electrified and opened, hydraulic oil enters the first active balance hydraulic cylinder 36 and the second active balance hydraulic cylinder 37 to push the piston rods to extend and retract, and at the moment, the spray rod suspension is in an active balance adjusting state; when the second two-position three-way proportional reversing valve 12 is opened, hydraulic oil enters a rod cavity of the profiling hydraulic cylinder 18 to push a piston rod of the hydraulic cylinder to retract, the spray rod is lifted, when the second two-position two-way proportional reversing valve 13 is opened, the piston rod of the hydraulic cylinder is pulled by the gravity of the spray rod to extend out, oil in the hydraulic cylinder returns to an oil tank, the spray rod descends, and at the moment, the spray rod suspension is in a ground profiling state.
(2) Load feedback and dynamic pressure feedback systems. The first sensing check valve 6, the second sensing check valve 15, the third sensing check valve 25, the fourth sensing check valve 26, the fifth sensing check valve 32 and the differential pressure type overflow valve 1 form a load feedback loop, the maximum load pressure on all the branches is fed back to a control oil port of the differential pressure type overflow valve 1 by each sensing check valve, the valve core of the differential pressure type overflow valve 1 is pushed by the pressure difference between the maximum load pressure and the pressure of an oil inlet, the flow of hydraulic oil flowing back to the oil tank is regulated, and therefore the flow entering the hydraulic cylinder is regulated.
The first damping throttle valve 7, the second damping throttle valve 16, the lifting energy accumulator 8 and the profiling energy accumulator 17 form a dynamic pressure feedback unit, the damping of the system can be increased through the dynamic pressure feedback unit, and the attenuation of the residual vibration after the posture of the spray rod is adjusted is facilitated.
(3) Spray lance height control, folding and anticollision. The height adjustment of the spray rod is the same as the working process of a hydraulic system in the ground profiling process; during folding, the first three-position five-way reversing valve 20 and the second three-position five-way reversing valve 28 control the piston rod of the related hydraulic cylinder to extend or retract, and the speed is adjusted by the first one-way throttle valve 29, the first throttle valve 19 and the second throttle valve 27; in the front anti-collision process, the safety valve 42 is opened, the oil flows back to the oil tank, the piston rod of the front anti-collision hydraulic cylinder 23 retracts, and the spray rod is turned backwards; during the rear collision avoidance process, the safety valve 42 is opened, the hydraulic oil flows back to the hydraulic oil tank, the piston rod of the folding hydraulic cylinder 24 extends out, and the spray rod is folded forward.
Claims (5)
1. The utility model provides a high ground clearance sprayer spray lance suspension control hydraulic system which characterized in that: the system comprises a differential pressure type overflow valve (1), a hydraulic pump (38), a lifting hydraulic unit, a left spray rod folding profiling hydraulic unit, a right spray rod folding profiling hydraulic unit and a vertical active and passive suspension control hydraulic unit;
the lifting hydraulic unit comprises a first differential pressure reducing valve (2), a first two-position three-way proportional directional valve (3), a first two-position two-way proportional directional valve (4), a first throttle hole (5), a first sensing one-way valve (6), a first lifting hydraulic cylinder (9) and a second lifting hydraulic cylinder (10);
an oil outlet of the first fixed differential pressure reducing valve (2) is connected with an oil inlet of the first two-position three-way proportional reversing valve (3); the oil outlet of the first two-position three-way proportional reversing valve (3) is respectively connected with a rodless cavity of the first lifting hydraulic cylinder (9) and a rodless cavity of the second lifting hydraulic cylinder (10); an oil inlet of the first throttling hole (5) is connected with a feedback oil port of the first fixed differential pressure reducing valve (2), and an oil outlet of the first throttling hole (5) is connected with an oil inlet of the first two-position two-way proportional reversing valve (4); the oil outlet of the first two-position two-way proportional reversing valve (4) is respectively connected with a rodless cavity of the first lifting hydraulic cylinder (9) and a rodless cavity of the second lifting hydraulic cylinder (10); an oil inlet of the first sensing check valve (6) is respectively connected with a feedback oil port of the first fixed differential pressure reducing valve (2) and a feedback oil port of the first two-position three-way proportional reversing valve (3), and an oil outlet of the first sensing check valve (6) is connected with a control oil port of the differential pressure overflow valve (1);
the left spray rod folding profiling hydraulic unit and the right spray rod folding profiling hydraulic unit are provided with the same component composition and a connecting loop, and both comprise a profiling unit, a folding unit and an extending unit;
the profiling unit comprises a second constant-differential pressure reducing valve (11), a second two-position three-way proportional reversing valve (12), a second two-position two-way proportional reversing valve (13), a second orifice (14), a second sensing one-way valve (15) and a profiling hydraulic cylinder (18);
an oil outlet of the second constant-differential pressure reducing valve (11) is connected with an oil inlet of a second two-position three-way proportional reversing valve (12), and an oil outlet of the second two-position three-way proportional reversing valve (12) is connected with a rod cavity of the profiling hydraulic cylinder (18); an oil inlet of the second throttling hole (14) is connected with a feedback oil port of the second constant-differential pressure reducing valve (11), and an oil outlet of the second throttling hole (14) is connected with an oil inlet of the second two-position two-way proportional reversing valve (13); an oil outlet of the second two-position two-way proportional reversing valve (13) is connected with a rod cavity of the profiling hydraulic cylinder (18); an oil inlet of the second sensing check valve (15) is respectively connected with a feedback oil port of the second constant-differential pressure reducing valve (11) and a feedback oil port of the second two-position three-way proportional reversing valve (12), and an oil outlet of the second sensing check valve (15) is connected with a control oil port of the differential pressure overflow valve (1);
the folding unit comprises a third sensing one-way valve (25), a first throttle valve (19), a first three-position five-way reversing valve (20) and a folding hydraulic cylinder (24);
an oil outlet of the first throttle valve (19) is connected with an oil inlet of a first three-position five-way reversing valve (20), and two oil outlets of the first three-position five-way reversing valve (20) are respectively connected with a rod cavity and a rodless cavity of a folding hydraulic cylinder (24); an oil inlet of the third sensing check valve (25) is connected with a sensing oil port of the first three-position five-way reversing valve (20), and an oil outlet of the third sensing check valve (25) is connected with a control oil port of the differential pressure type overflow valve (1);
the extension unit comprises a fourth sensing one-way valve (26), a second throttle valve (27), a second three-position five-way reversing valve (28), a first one-way throttle valve (29) and an extension hydraulic cylinder (30);
the oil outlet of the second throttle valve (27) is connected with the oil inlet of a second three-position five-way reversing valve (28), two oil outlets of the second three-position five-way reversing valve (28) are respectively connected with the oil inlet of a first one-way throttle valve (29), and the oil outlets of the two first one-way throttle valves (29) are respectively connected with a rod cavity and a rodless cavity of an extension hydraulic cylinder (30); an oil inlet of the fourth sensing check valve (26) is connected with a sensing oil port of the second three-position five-way reversing valve (28), and an oil outlet of the fourth sensing check valve is connected with a control oil port of the differential pressure type overflow valve (1);
the vertical active and passive suspension control hydraulic unit comprises a third constant-differential pressure reducing valve (31), a fifth sensing one-way valve (32), a three-position five-way proportional reversing valve (33), a two-position two-way electromagnetic valve (34), a second one-way throttle valve (35), a first active balancing hydraulic cylinder (36) and a second active balancing hydraulic cylinder (37);
the oil outlet of the third constant-differential pressure reducing valve (31) is connected with the oil inlet of a three-position five-way proportional reversing valve (33), two oil outlets of the three-position five-way proportional reversing valve (33) are respectively connected with the oil inlet of a two-position two-way electromagnetic valve (34), the oil outlets of the two-position two-way electromagnetic valves (34) are respectively connected with the oil inlet of a second one-way throttle valve (35), and the oil outlets of the two second one-way throttle valves (35) are respectively connected with a rodless cavity of a first active balancing hydraulic cylinder (36) and a rodless cavity of a second active balancing hydraulic cylinder (37); an oil inlet of the fifth sensing check valve (32) is connected with a feedback oil port of the third constant-differential pressure reducing valve (31), and an oil outlet of the fifth sensing check valve (32) is connected with a control oil port of the differential pressure overflow valve (1);
an oil inlet of the hydraulic pump (38) is connected with a hydraulic oil tank (41) through an oil outlet filter (40), and an oil outlet of the hydraulic pump (38) is respectively connected with an oil inlet of the differential pressure type overflow valve (1), an oil inlet of the first constant differential pressure reduction valve (2), an oil inlet of the second constant differential pressure reduction valve (11), an oil inlet of the first throttle valve (19), an oil inlet of the second throttle valve (27) and an oil inlet of the third constant differential pressure reduction valve (31);
an oil return port of the differential pressure type overflow valve (1), an oil return port of the first two-position two-way proportional reversing valve (4), an oil return port of the second two-position two-way proportional reversing valve (13), an oil return port of the first three-position five-way reversing valve (20), an oil return port of the second three-position five-way reversing valve (28) and an oil return port of the three-position five-way proportional reversing valve (33) are connected with a hydraulic oil tank (41) through an oil return filter (39);
the differential pressure type overflow valve (1), a first sensing one-way valve (6) of the lifting hydraulic unit, a second sensing one-way valve (15), a third sensing one-way valve (25) and a fourth sensing one-way valve (26) of the left spray rod folding profiling hydraulic unit and the right spray rod folding profiling hydraulic unit, and a fifth sensing one-way valve (32) of the vertical active and passive suspension control hydraulic unit jointly form a load feedback loop.
2. The high clearance sprayer boom suspension control hydraulic system of claim 1, characterized in that: the boom suspension control hydraulic system of the high-ground-clearance spraying machine further comprises a front anti-collision valve (21), a front anti-collision hydraulic cylinder (23) and a pair of rear anti-collision valves (22);
the two rear anti-collision valves (22) are respectively arranged on oil paths of two oil outlets of a first three-position five-way reversing valve (20) in a folding unit of the left spray rod folding profiling hydraulic unit and a folding unit of the right spray rod folding profiling hydraulic unit and a rod cavity and a rodless cavity of the folding hydraulic cylinder (24), wherein the two oil outlets of the first three-position five-way reversing valve (20) are respectively connected with an oil inlet and an oil return port of the rear anti-collision valve (22), and the two oil outlets of the rear anti-collision valve (22) are respectively connected with the rod cavity and the rodless cavity of the folding hydraulic cylinder (24);
an oil inlet of the front anti-collision valve (21) is connected with an oil outlet of a first three-position five-way reversing valve (20) in a folding unit of the left spray rod folding profiling hydraulic unit or a folding unit of the right spray rod folding profiling hydraulic unit, and an oil outlet of the front anti-collision valve (21) is connected with a rodless cavity of a front anti-collision hydraulic cylinder (23).
3. The high clearance sprayer boom suspension control hydraulic system of claim 1, characterized in that: the oil circuit between the first lifting hydraulic cylinder (9) and the first two-position three-way proportional reversing valve (3) is provided with a first dynamic pressure feedback unit, the first dynamic pressure feedback unit comprises a first damping throttle valve (7) and a lifting energy accumulator (8), an oil inlet of the first damping throttle valve (7) is connected to the oil circuit between the first lifting hydraulic cylinder (9) and the first two-position three-way proportional reversing valve (3), and an oil outlet of the first damping throttle valve (7) is connected with the lifting energy accumulator (8).
4. The high clearance sprayer boom suspension control hydraulic system of claim 1, characterized in that: and a second dynamic pressure feedback unit is arranged on an oil path between the profiling hydraulic cylinder (18) and the second two-position three-way proportional reversing valve (12), the second dynamic pressure feedback unit comprises a second damping throttle valve (16) and a profiling energy accumulator (17), an oil inlet of the second damping throttle valve (16) is connected to the oil path between the profiling hydraulic cylinder (18) and the second two-position three-way proportional reversing valve (12), and an oil outlet is connected with the profiling energy accumulator (17).
5. The high clearance sprayer boom suspension control hydraulic system of claim 1, characterized in that: and a safety valve (42) is arranged on the load feedback loop, and an oil return port of the safety valve (42) is connected to an oil return path of an oil return port of the differential pressure type overflow valve (1).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201810816802.8A CN108835092B (en) | 2018-07-24 | 2018-07-24 | High-clearance sprayer spray rod suspension control hydraulic system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201810816802.8A CN108835092B (en) | 2018-07-24 | 2018-07-24 | High-clearance sprayer spray rod suspension control hydraulic system |
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| Publication Number | Publication Date |
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| CN108835092A CN108835092A (en) | 2018-11-20 |
| CN108835092B true CN108835092B (en) | 2020-07-31 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111852965B (en) * | 2020-06-17 | 2022-08-09 | 中国北方车辆研究所 | Pressure-displacement comprehensive control system and control method based on rocker arm suspension |
| CN115095563A (en) * | 2022-06-15 | 2022-09-23 | 山东思代尔农业装备有限公司 | Hydraulic synchronous control system of lifting and folding mechanism of spraying machine |
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| GB704661A (en) * | 1948-11-11 | 1954-02-24 | Leslie Hubert Watson | Improvements in spraying devices, particularly for agricultural and like purposes |
| CN102091682A (en) * | 2010-12-24 | 2011-06-15 | 江苏大学 | Self-balancing spray boom spraying machine |
| KR20120140626A (en) * | 2011-06-21 | 2012-12-31 | 카야바 고교 가부시기가이샤 | Boom sprayer and boom vibration damping device |
| CN103004736A (en) * | 2012-12-31 | 2013-04-03 | 山东农业大学 | Three-in-one multifunctional spraying machine and three-station conversion method |
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| US4358054A (en) * | 1978-08-31 | 1982-11-09 | Ehrat Arthur H | Field-sprayer tank-vehicle having means for on-site metering and mixing of soil-treating chemicals |
| DE20113172U1 (en) * | 2001-08-08 | 2001-12-13 | Posselt, Stefan, 83512 Wasserburg | Work and transport frames |
| CA2487184C (en) * | 2004-11-05 | 2012-04-10 | Stanislaus Montgomery Shivak | Boom control system |
| CN201911089U (en) * | 2010-11-29 | 2011-08-03 | 现代农装科技股份有限公司 | Hydraulic system of self-propelled cotton top-cutting machine |
| CN105971953B (en) * | 2016-06-27 | 2017-11-14 | 中国农业大学 | A kind of spraying machine spray lance ground shape imitation hydraulic system with dynamic pressure feedback device |
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| GB443618A (en) * | 1935-02-14 | 1936-03-03 | Arthur Alfred Mee | Improvements in or relating to apparatus for spraying liquids |
| GB704661A (en) * | 1948-11-11 | 1954-02-24 | Leslie Hubert Watson | Improvements in spraying devices, particularly for agricultural and like purposes |
| CN102091682A (en) * | 2010-12-24 | 2011-06-15 | 江苏大学 | Self-balancing spray boom spraying machine |
| KR20120140626A (en) * | 2011-06-21 | 2012-12-31 | 카야바 고교 가부시기가이샤 | Boom sprayer and boom vibration damping device |
| CN103004736A (en) * | 2012-12-31 | 2013-04-03 | 山东农业大学 | Three-in-one multifunctional spraying machine and three-station conversion method |
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