CN108035945A - Control valve group for the output of quantitative system flow proportional - Google Patents
Control valve group for the output of quantitative system flow proportional Download PDFInfo
- Publication number
- CN108035945A CN108035945A CN201810013073.2A CN201810013073A CN108035945A CN 108035945 A CN108035945 A CN 108035945A CN 201810013073 A CN201810013073 A CN 201810013073A CN 108035945 A CN108035945 A CN 108035945A
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- CN
- China
- Prior art keywords
- valve
- control valve
- proportional
- working holes
- flow
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000012530 fluid Substances 0.000 claims abstract description 39
- 230000008676 import Effects 0.000 claims description 9
- 238000004891 communication Methods 0.000 claims description 6
- 238000013016 damping Methods 0.000 claims description 2
- 230000033001 locomotion Effects 0.000 abstract description 15
- 238000006073 displacement reaction Methods 0.000 abstract description 13
- 238000000034 method Methods 0.000 abstract description 4
- 239000002131 composite material Substances 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 24
- 239000000725 suspension Substances 0.000 description 6
- 239000007788 liquid Substances 0.000 description 5
- 239000002828 fuel tank Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000001276 controlling effect Effects 0.000 description 2
- 230000005611 electricity Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000007667 floating Methods 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000003971 tillage Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
- F15B21/087—Control strategy, e.g. with block diagram
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The present invention relates to hydraulic technique, more particularly to a kind of control valve group for the output of quantitative system flow proportional, it includes operated proportional flow control valve, proportional reversing valve, pressure compensator, permanent flow valve, check valve and P hydraulic fluid ports, T hydraulic fluid ports, A1 working holes, A2 working holes, B1 working holes, B2 working holes.This valve group realizes that the movement velocity displacement of executing agency accurately controls, while executing agency's movement velocity is from workload pressure influence by controlling the input signal of operated proportional flow control valve；It by adjusting each operated proportional flow control valve valve port size, can work at the same time multiple executing agencies, complete composite move, be influenced from load pressure.
Description
Technical field
The present invention relates to hydraulic technique, more particularly to a kind of control valve group for the output of quantitative system flow proportional.
Background technology
In Practical Project machinery or industrial hydraulic system, in order to accurately control output flow, become mostly using load-sensitive
Amount system, but this system cost is higher, use condition is harsh, and debugging is difficult.And quantitatively system price is cheap, maintenance side
Just, it is subject to extensive use, but its control mode passes through regulating valve stem throttling channel aperture, control mainly using by-pass throttle
Output flow.But this control mode is influenced substantially by load change, and executing agency accurately controls difficulty.
The content of the invention
In view of the above-mentioned problems, the goal of the invention of the present invention is to provide, a kind of cost is low, flow control accuracy is high is used for
The control valve group of quantitative system flow proportional output.
To achieve the above object of the invention, the technical scheme is that：It is a kind of to be used for what quantitative system flow proportional exported
Control valve group, its include operated proportional flow control valve, proportional reversing valve, pressure compensator, permanent flow valve, check valve and P hydraulic fluid ports,
T hydraulic fluid ports, A1 working holes, A2 working holes, B1 working holes, B2 working holes；
The P hydraulic fluid ports are respectively communicated with the import of operated proportional flow control valve, pressure compensator, the outlet point of operated proportional flow control valve
Not through check valve connection A1 working holes, A2 working holes, B1 working holes, B2 working holes, A1 working holes, A2 working holes, B1 working holes,
B2 working holes are connected through proportional reversing valve with T hydraulic fluid ports respectively, are taken after the spring cavity of pressure compensator and the inlet communication of permanent flow valve
The load signal of operated proportional flow control valve outlet；Pressure compensator is connected with the outlet of permanent flow valve with T hydraulic fluid ports, P hydraulic fluid ports and T hydraulic fluid ports
Between be equipped with overflow valve.
It is preferred that the check valve between the operated proportional flow control valve outlet and working hole keeps check valve for load.
It is preferred that damping hole is equipped between the permanent flow valve import and pressure compensator spring cavity.
It is preferred that after the inlet communication of the pressure compensator and permanent flow valve, proportional flow control is taken by unidirectional valve group
The outlet load signal of valve.
It is preferred that after the inlet communication of the pressure compensator and permanent flow valve, operated proportional flow control valve is taken by shuttle valve group
Outlet load signal.
The beneficial effects of the present invention are：
（1）Executing agency's speed displacement accurately controls：By controlling the input signal of operated proportional flow control valve, executing agency is realized
Movement velocity displacement accurately control, while executing agency's movement velocity is from workload pressure influence.
（2）Executing agency can composite move：Four operated proportional flow control valve oil inlet parallel connection oil inlets, by adjusting each ratio
Example flow control valve valve port size, can work at the same time multiple executing agencies, complete composite move, be influenced from load pressure.
（3）Low-pressure load discharge：After executing agency completes movement, the fluid of pressure compensator control spring cavity is returned by permanent flow valve
Fuel tank so that system fluid makes system more energy saving by pressure compensator Low-pressure load discharge.
（4）The accurate control of output flow is realized with quantitative system, from the influence of load change, whole system cost
Low, easy to maintain, use scope is extensive.
Brief description of the drawings
Fig. 1 is the schematic diagram of the embodiment of the present invention one；
Fig. 2 is the schematic diagram of the embodiment of the present invention two；
Fig. 3 is applied to agricultural machinery suspension and leveling system schematic diagram for the present invention.
Description of symbols in figure：
101- operated proportional flow control valves I, 102- operated proportional flow control valve II, 103- operated proportional flow control valve III, 104- ratio stream
Control valve IV, 105- overflow valve, 106- pressure compensators, 107- permanent flow valves, 108- proportional reversing valves, 109- check valve I,
110- check valves II, 111- electric-control stop valve, 112- check valves III, 113- check valve IV, 114- electric-control stop valve, 115- are mono-
To valve V, 116- check valves VI, 117- proportional reversing valve, 118- check valves VII, 119- check valve VIII；120- shuttle valves I, 121-
Shuttle valve II, 122- shuttle valve III, and A1 hydraulic fluid ports, A2 hydraulic fluid ports, B1 hydraulic fluid ports, B2 hydraulic fluid ports, T hydraulic fluid ports, P2 hydraulic fluid ports；
1- flow proportional output control valve group I, 2- high pressure filters, 3- hydraulic gear pumps, 4- oil absorption filters, 5- liquid level liquid temperatures
Meter, 6- hydraulic air filters, 7- hydraulic oil containers, 8- work switching valve groups, 9- quick-release connectors, 10- clutch for clutch control valves, 11- liquid
Press clutch, 12- accumulators, 13- quick-release connectors, 14- flow proportional output control valve group II, 15- vehicle body support oil cylinders, 16-
Shut-off valve, 17-, which meets an urgent need, is manually operated valve group, the right lift cylinder of 18- suspension, the left lift cylinder of 19- suspension.
Embodiment
To further understand the present invention, technical scheme is done with reference to the accompanying drawings and detailed description into one
Step explanation, referring to Fig. 1, Fig. 2.
In the present embodiment, as shown in Figure 1, the P2 hydraulic fluid ports of flow proportional output control valve group connect four ratio streams respectively
The import of control valve 101/102/103/104, the import of overflow valve 105 and the import of pressure compensator 106；Proportional flow control
The outlet of valve 101 processed is connected through check valve 119 and 117 import of proportional reversing valve and A1 hydraulic fluid ports, and operated proportional flow control valve 102 goes out
Mouth is connected through check valve 116 and 114 import of electric-control stop valve and B1 hydraulic fluid ports, and proportional reversing valve 117 goes out with electric-control stop valve 114
Mouth is connected to T1 mouthfuls；The connection mode of operated proportional flow control valve 103 and operated proportional flow control valve 104 with it is above similar；Four ratios
Hydraulic control of the outlet through check valve 109/112/115/118 Yu pressure compensator 106 of example flow control valve 101/102/103/104
Chamber is connected with 107 entrance of permanent flow valve, and 106 outlets of pressure compensator are connected in T1 mouthfuls with the outlet of permanent flow valve 106.
By taking the present invention is applied to agricultural machinery suspension and leveling system as an example, as shown in Fig. 2, the gear pump 3 of quantitative system passes through
High pressure filter 2 connects work switching valve group 8, and the Pz1 hydraulic fluid ports of work switching valve group 8 connect clutch for clutch control valve group through quick-release connector
10 Pz2 hydraulic fluid ports；The P3 mouths of the A mouths connection vehicle attitude control valve group 14 of work switching valve group 8, B mouthfuls of connections lift control valve group 1
P2 mouthfuls；A3-A6 hydraulic fluid ports of flow proportional output control valve group II14 connect 15 big chamber of vehicle body support oil cylinder respectively；Lifting control
B1 the and B2 hydraulic fluid ports of valve group 1 connect the big chamber of lift cylinder respectively, A1 and A2 hydraulic fluid ports connect the small chamber of lift cylinder respectively；Clutch control
The Az mouth connections hydraulic clutch 11 of valve group 10 processed, Af mouthfuls connect accumulator 12, and T mouthfuls take back fuel tank 7.Flow proportional output control valve
Group III is used to control suspension lift cylinder, adjusts the stroke of left and right lift cylinder, realizes agricultural equipment tillage resistance, ploughs
Gesture（Height and angle）Automatic adjusument.Flow proportional output control valve group II14 is used to adjust vehicle body support oil cylinder,
Tractor is set to keep vehicle body horizontal at larger hillside fields, clutch for clutch control valve group 10 controls the hydraulic clutch 11 of tractor.
Embodiment one and embodiment two differ only in check valve I109, check valve III112, check valve V115 shuttle valves
I120, shuttle valve II 121, shuttle valve III122 are replaced.
The present invention operation principle be：
When suspension is lifted, illustrate by taking the movement of right lift cylinder as an example.
（1）When oil cylinder lifts, the electromagnet of the operated proportional flow control valve 104 in flow proportional output control valve group I obtain it is electric,
And according to oil cylinder Displacement Feedback Signal Regulation valve port opening, pump discharge fluid through operated proportional flow control valve 104, check valve 110 into
Enter the big chamber of lift cylinder, oil cylinder stretches out, when cylinder movement to designated displacement, the control proportional flow control of displacement sensor feedback signal
Valve 104 processed is closed, and cylinder movement stops, and the unnecessary fluid of pump in motion process is through 106 off-load oil return box of pressure compensator；It is automatically controlled
111 electromagnet of shut-off valve obtains electric, is operated in right position in figure, the small chamber fluid of hydraulic cylinder returns to fuel tank through electric-control stop valve 111.
（2）When oil cylinder declines, before farm implements are contacted with ground, the electromagnet of proportional reversing valve 108 adjusts proportioning valve and opens
Mouth size, control cylinder decrease speed and displacement, the work of electromagnet of 103 control valve of the 3rd proportional flow is in maximum control at this time
Electric current, valve port standard-sized sheet, pump discharge fluid enter the small chamber of lift cylinder, big chamber oil through operated proportional flow control valve 103, check valve 113
Liquid returns to fuel tank through proportional reversing valve 108.
（3）After farm implements are contacted with ground, the work of electromagnet of proportional reversing valve 108 is complete in maximum controlling current, valve port
Open, the electromagnet of operated proportional flow control valve 103 adjusts proportioning valve valve port size according to oil cylinder Displacement Feedback signal at this time, and then
Control cylinder moving displacement and speed, the unnecessary fluid of pump during the motion is through 106 off-load oil return box of pressure compensator.Work as oil
Cylinder movement terminates, all electromagnet dead electricity, and oil cylinder load pressure is through 107 off-load of permanent flow valve, and pump discharge fluid is through 3-position 4-way electricity
803 middle position off-load oil return box of magnetic reversal valve.
（4）Floating bit：At the same time must be electric with electric-control stop valve 111 when lifting the proportional reversing valve 108 in valve group, two valves are all
Right position in figure is operated in, the big chamber of oil cylinder is connected with small chamber at this time, and system is operated in quick condition.
（5）During vehicle attitude control, to illustrate from right to left exemplified by first cylinder movement in scheming.
The electromagnet of operated proportional flow control valve 1401 obtains electric in flow proportional output control valve group II14, and according to vehicle body branch
Leg oil cylinder Displacement Feedback signal, adjust operated proportional flow control valve openings of sizes, control cylinder moving displacement, pump discharge fluid through than
Example flow control valve 1401, check valve 1407 enter the big chamber of support oil cylinder, and oil cylinder stretches out, when cylinder movement to designated displacement, position
Displacement sensor feedback signal control operated proportional flow control valve 1401 is closed, and cylinder movement stops, the more excess oil of pump in motion process
Liquid is through 1403 off-load oil return box of pressure compensator.When support oil cylinder declines, the work of electromagnet of operated proportional flow control valve 1401
In maximum current, valve port standard-sized sheet, the electromagnet of proportional reversing valve 1405 obtains electric, and adjusts valve port size, reduction of speed under control cylinder
Degree.
Claims (5)
- A kind of 1. control valve group for the output of quantitative system flow proportional, it is characterised in that：Include operated proportional flow control valve, Proportional reversing valve, pressure compensator, permanent flow valve, check valve and P hydraulic fluid ports, T hydraulic fluid ports, A1 working holes, A2 working holes, B1 work Mouth, B2 working holes；The P hydraulic fluid ports are respectively communicated with the import of operated proportional flow control valve, pressure compensator, the outlet point of operated proportional flow control valve Not through check valve connection A1 working holes, A2 working holes, B1 working holes, B2 working holes, A1 working holes, A2 working holes, B1 working holes, B2 working holes are connected through proportional reversing valve with T hydraulic fluid ports respectively, are taken after the spring cavity of pressure compensator and the inlet communication of permanent flow valve The load signal of operated proportional flow control valve outlet；Pressure compensator is connected with the outlet of permanent flow valve with T hydraulic fluid ports, P hydraulic fluid ports and T hydraulic fluid ports Between be equipped with overflow valve.
- 2. the control valve group according to claim 1 for the output of quantitative system flow proportional, it is characterised in that：Described The check valve that operated proportional flow control valve is exported between working hole keeps check valve for load.
- 3. the control valve group according to claim 1 for the output of quantitative system flow proportional, it is characterised in that：The perseverance Damping hole is equipped between stream valve import and pressure compensator spring cavity.
- 4. the control valve group according to claim 1 for the output of quantitative system flow proportional, it is characterised in that：The pressure After the inlet communication of force compensating device and permanent flow valve, the outlet load signal of operated proportional flow control valve is taken by unidirectional valve group.
- 5. the control valve group according to claim 1 for the output of quantitative system flow proportional, it is characterised in that：The pressure After the inlet communication of force compensating device and permanent flow valve, the outlet load signal of operated proportional flow control valve is taken by shuttle valve group.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810013073.2A CN108035945B (en) | 2018-01-07 | 2018-01-07 | Control valve group for quantitative system flow proportion output |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810013073.2A CN108035945B (en) | 2018-01-07 | 2018-01-07 | Control valve group for quantitative system flow proportion output |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108035945A true CN108035945A (en) | 2018-05-15 |
| CN108035945B CN108035945B (en) | 2024-04-09 |
Family
ID=62098906
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810013073.2A Active CN108035945B (en) | 2018-01-07 | 2018-01-07 | Control valve group for quantitative system flow proportion output |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108035945B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110411526A (en) * | 2019-08-14 | 2019-11-05 | 杭州启飞智能科技有限公司 | A kind of accumulative medicine calculation method of plant protection drone |
| CN112985872A (en) * | 2021-05-20 | 2021-06-18 | 成都康拓兴业科技有限责任公司 | Oil mist separation and transportation test bed and test method of aviation oil mist separator |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS646502A (en) * | 1987-06-30 | 1989-01-11 | Hitachi Construction Machinery | Hydraulic circuit apparatus controlled by load sensing |
| US20130146162A1 (en) * | 2010-05-11 | 2013-06-13 | Parker-Hannifin Corporation | Pressure Compensated Hydraulic System Having Differential Pressure Control |
| CN103671335A (en) * | 2013-12-19 | 2014-03-26 | 杭叉集团股份有限公司 | Load-sensitive electric proportional multi-loop valve |
| CN106032261A (en) * | 2016-07-20 | 2016-10-19 | 浙江大学 | Tension control device of high-power hydraulic winch |
| CN207750316U (en) * | 2018-01-07 | 2018-08-21 | 浙江高宇液压机电有限公司 | Control valve group for the output of quantitative system flow proportional |
-
2018
- 2018-01-07 CN CN201810013073.2A patent/CN108035945B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS646502A (en) * | 1987-06-30 | 1989-01-11 | Hitachi Construction Machinery | Hydraulic circuit apparatus controlled by load sensing |
| US20130146162A1 (en) * | 2010-05-11 | 2013-06-13 | Parker-Hannifin Corporation | Pressure Compensated Hydraulic System Having Differential Pressure Control |
| CN103671335A (en) * | 2013-12-19 | 2014-03-26 | 杭叉集团股份有限公司 | Load-sensitive electric proportional multi-loop valve |
| CN106032261A (en) * | 2016-07-20 | 2016-10-19 | 浙江大学 | Tension control device of high-power hydraulic winch |
| CN207750316U (en) * | 2018-01-07 | 2018-08-21 | 浙江高宇液压机电有限公司 | Control valve group for the output of quantitative system flow proportional |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110411526A (en) * | 2019-08-14 | 2019-11-05 | 杭州启飞智能科技有限公司 | A kind of accumulative medicine calculation method of plant protection drone |
| CN112985872A (en) * | 2021-05-20 | 2021-06-18 | 成都康拓兴业科技有限责任公司 | Oil mist separation and transportation test bed and test method of aviation oil mist separator |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108035945B (en) | 2024-04-09 |
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