CN109139598A - A kind of double valve-regulated load port separate control valves based on the compensation of machine hydraulic pressure difference - Google Patents
A kind of double valve-regulated load port separate control valves based on the compensation of machine hydraulic pressure difference Download PDFInfo
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- CN109139598A CN109139598A CN201810964378.1A CN201810964378A CN109139598A CN 109139598 A CN109139598 A CN 109139598A CN 201810964378 A CN201810964378 A CN 201810964378A CN 109139598 A CN109139598 A CN 109139598A
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- valve
- port
- control valves
- pressure line
- separate control
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- 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
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- 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
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- 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
- F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40576—Assemblies of multiple valves
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/455—Control of flow in the feed line, i.e. meter-in control
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The present invention relates to Fluid Transmission and Control technical fields, especially a kind of double valve-regulated load port separate control valves based on the compensation of machine hydraulic pressure difference, including secondary relief one, secondary relief two, two position, three-way electromagnetic change valve one, two position, three-way electromagnetic change valve two, 3-position-3-way solenoid directional control valve one, 3-position-3-way solenoid directional control valve two, shuttle valve, uniform-pressure-drop valve, two-position two-way electromagnetic directional valve and integrated valve block, the present invention controls the same actuator using two 3-position-3-way solenoid directional control valves, to realize double valve-regulated load port independent controls, herein on basis, machine pressure difference compensation is carried out using 3-position-3-way solenoid directional control valve of the uniform-pressure-drop valve to import oil circuit, to realize the ratio control of inlet flow rate.
Description
Technical field
The present invention relates to Fluid Transmission and Control technical field, specific field is a kind of bivalve based on the compensation of machine hydraulic pressure difference
Control formula load port separate control valves.
Background technique
The valve control hydraulic system of traditional engineering machinery, agricultural machinery and industrial machinery, is all made of a polygon throttling
Primary control spool control the import and export oil circuit of hydraulic actuator simultaneously, during inlet throttle speed regulation, outlet is simultaneously
It throttles, which results in the losses of extra outlet throttling.Therefore, although traditional valve control system can reach preferable movement
Control effect, but makes that system energy consumption is big, low efficiency to a certain extent.In order to overcome conventional valve draining pressure system effectiveness low
There is hydraulic actuator import and export independent control load port independent control technology, is utilized respectively multiple spools to hydraulic in problem
Actuator import and export oil circuit is independently controlled, and the both direction of hydraulic actuator is completed by different control logics
Motion control can take into account outlet pressure control, while completing inlet throttle speed regulating control so as to avoid conventional valve control
Duplicate restriction loss in hydraulic system.
Load port autonomous control system is a typical multi-input multi-output control system, and there is pressure, flow
Coupling control, is a control system complicated and changeable.Currently, in the flow control in load port autonomous control system,
Flow control is carried out using " electro-hydraulic pressure difference compensation method ", spool displacement is detected by built-in valve core displacement sensor and with electricity
The mode of feedback realizes flow control, and such control method is complicated, more demanding to controller, and need largely to test into
Row performance adjustment, therefore, it is difficult to be promoted and applied in the hydraulic system of industrial machinery.
Summary of the invention
The purpose of the present invention is to provide a kind of double valve-regulated load port separate control valves based on the compensation of machine hydraulic pressure difference, with
It is complicated to solve flow control methods in the prior art, it is more demanding to controller, it is not easy the problem of realizing.
To achieve the above object, the invention provides the following technical scheme: it is a kind of based on the double valve-regulated of machine hydraulic pressure difference compensation
Load port separate control valves include first and second overflow valve two of secondary relief, two position, three-way electromagnetic change valve one, two-position three way electricity
Magnetic reversal valve two, 3-position-3-way solenoid directional control valve one, 3-position-3-way solenoid directional control valve two, shuttle valve, uniform-pressure-drop valve, bi-bit bi-pass
Solenoid directional control valve and integrated valve block；
The first oil inlet, the second oil inlet, the first oil return opening, the second oil return opening, first negative is drilled on the integrated valve block
Carry sensitive hydraulic fluid port, the second load-sensitive hydraulic fluid port, the first actuator port and the second actuator port, first oil inlet and second into
Hydraulic fluid port connection, first oil return opening and the connection of the second oil return opening；
The oil inlet of the uniform-pressure-drop valve and the first oil inlet, the second oil inlet of integrated valve block pass through fluid pressure line phase
Even, the actuator port of the uniform-pressure-drop valve, the oil inlet of 3-position-3-way solenoid directional control valve one and 3-position-3-way solenoid directional control valve
Two oil inlet is connected by fluid pressure line, oil return opening, the 3-position-3-way solenoid directional control valve two of 3-position-3-way solenoid directional control valve one
Oil return opening be connected with the first oil return opening of integrated valve block, the second oil return opening by fluid pressure line, 3-position-3-way solenoid directional control valve
One actuator port, the actuator port of two-position two-way electromagnetic directional valve, two position, three-way electromagnetic change valve two oil inlet, secondary overflow
The oil inlet of stream valve one is connected with the first actuator port of integrated valve block by fluid pressure line, 3-position-3-way solenoid directional control valve two
Actuator port, the oil inlet of two-position two-way electromagnetic directional valve, the oil return opening of two position, three-way electromagnetic change valve two, secondary relief two
Oil inlet be connected with the second actuator port of integrated valve block by fluid pressure line, it is the actuator port of secondary relief one, secondary
The actuator port of overflow valve two, the first oil return opening of the oil inlet of two position, three-way electromagnetic change valve one and integrated valve block, second time
Hydraulic fluid port is connected by fluid pressure line, the work of the oil return opening and two position, three-way electromagnetic change valve two of two position, three-way electromagnetic change valve one
Hydraulic fluid port by fluid pressure line be connected, the actuator port of two position, three-way electromagnetic change valve one, the first of shuttle valve compare hydraulic fluid port with calmly it is poor
The control port of pressure reducing valve is connected by fluid pressure line, and the output oil port of shuttle valve and the first load-sensitive hydraulic fluid port of integrated valve block are logical
It crosses fluid pressure line to be connected, the minus second load-sensitive hydraulic fluid port that the second of shuttle valve compares hydraulic fluid port and integrated valve block passes through fluid pressure line phase
Even.
Preferably, the secondary relief one includes check valve and overflow valve, the oil outlet and overflow valve of the check valve
Oil outlet the actuator port of secondary relief one, the oil inlet and overflow valve of the check valve are connected to form by fluid pressure line
Oil inlet the oil inlet of secondary relief one is connected to form by fluid pressure line.
Preferably, the structure of the secondary relief two is consistent with the structure of secondary relief one.
A kind of hydraulic system for double valve-regulated load port separate control valves that application is compensated based on machine hydraulic pressure difference, including it is hydraulic
Cylinder, the first separate control valves, fuel tank, variable pump, the second separate control valves and hydraulic motor, the of first separate control valves
Two oil return openings are connected with the first oil return opening of the second separate control valves by fluid pressure line, and common oil return opening is formed, and first is independent
Second oil inlet of control valve is connected with the first oil inlet of the second separate control valves by fluid pressure line, and common oil inlet is formed
Mouthful, the second load-sensitive hydraulic fluid port of the first separate control valves passes through hydraulic with the first load-sensitive hydraulic fluid port of the second separate control valves
Pipeline is connected, and forms mutual load sensitivity hydraulic fluid port, and the inlet port of variable pump is connected with fuel tank by fluid pressure line, and variable pump goes out
Hydraulic fluid port is connected with the first oil inlet of the first separate control valves by fluid pressure line, and the load-sensitive hydraulic fluid port of variable pump and first is solely
First load-sensitive hydraulic fluid port of vertical control valve is connected by fluid pressure line, and the second oil return opening of the second separate control valves passes through hydraulic
Pipeline is connected with fuel tank, the first oil return opening of the first separate control valves, the second load-sensitive hydraulic fluid port of the second separate control valves,
Second oil inlet of two separate control valves is blocked by plug, and the of the first actuator port of the first separate control valves and hydraulic cylinder
One actuator port is connected by fluid pressure line, the second actuator port of the first separate control valves and the second actuator port of hydraulic cylinder
It is connected by fluid pressure line, the first actuator port of the first actuator port of the second separate control valves and hydraulic motor passes through hydraulic
Pipeline is connected, and the second actuator port of the second separate control valves passes through fluid pressure line phase with the second actuator port of hydraulic motor
Even.
Compared with prior art, the beneficial effects of the present invention are: the application utilizes two 3-position-3-way solenoid directional control valve controls
The same actuator is made, so that realizing double valve-regulated load port independent controls utilizes uniform-pressure-drop valve pair herein on basis
The 3-position-3-way solenoid directional control valve of import oil circuit carries out machine pressure difference compensation, to realize the ratio control of inlet flow rate, this Shen
Please not only with the characteristic of load port independent control, and effectively prevent the spool position in conventional load mouth autonomous control system
Detection is moved, robustness is good, practical during control, does not need to carry out special processing to control valve core, be related to
Hydraulic Elements can be realized using conventional inserted valve.
Detailed description of the invention
Fig. 1 is the schematic diagram of double valve-regulated load port separate control valves based on the compensation of machine hydraulic pressure difference；
Fig. 2 is the schematic diagram of secondary relief；
Fig. 3 is the principle using the hydraulic system of the double valve-regulated load port separate control valves compensated based on machine hydraulic pressure difference
Figure；
Fig. 4 is the principle frame using the hydraulic system of the double valve-regulated load port separate control valves compensated based on machine hydraulic pressure difference
Figure.
In figure: 1.1, secondary relief one, 1.2, secondary relief two, 2.1, two position, three-way electromagnetic change valve one, 2.2,
Two position, three-way electromagnetic change valve two, 3.1,3-position-3-way solenoid directional control valve one, 3.2,3-position-3-way solenoid directional control valve two, 4, shuttle
Valve, 5, uniform-pressure-drop valve, 6, two-position two-way electromagnetic directional valve, 7, integrated valve block, 8, hydraulic cylinder, the 9, first separate control valves, 10,
Fuel tank, 11, variable pump, the 12, second separate control valves, 13, hydraulic motor, 101, check valve, 102, overflow valve.
Specific embodiment
Following will be combined with the drawings in the embodiments of the present invention, and technical solution in the embodiment of the present invention carries out clear, complete
Site preparation description, it is clear that described embodiments are only a part of the embodiments of the present invention, instead of all the embodiments.It is based on
Embodiment in the present invention, it is obtained by those of ordinary skill in the art without making creative efforts every other
Embodiment shall fall within the protection scope of the present invention.
The present invention provides a kind of technical solution referring to FIG. 1-2: a kind of double valve-regulated loads based on the compensation of machine hydraulic pressure difference
Mouth separate control valves include secondary relief 1, secondary relief 2 1.2, two position, three-way electromagnetic change valve one 2.1, two
Three-way solenoid valve 2 2.2,3-position-3-way solenoid directional control valve 2 3.2, shuttle valve 4, is determined 3-position-3-way solenoid directional control valve 1
Difference pressure-reducing valve 5, two-position two-way electromagnetic directional valve 6 and integrated valve block 7；The first oil inlet P 1, the second oil inlet are drilled on integrated valve block 7
Mouth P2, the first oil return inlet T 1, the second oil return inlet T 2, the first load-sensitive hydraulic fluid port LS1, the second load-sensitive hydraulic fluid port LS2, the first work
Make hydraulic fluid port A and the second actuator port B, the first oil inlet P 1 is connected to the second oil inlet P 2, the first oil return inlet T 1 and the second oil return
Mouth T2 connection；The oil inlet P of uniform-pressure-drop valve 5 and the first oil inlet P 1, the second oil inlet P 2 of integrated valve block 7 pass through hydraulic tube
Road is connected, the actuator port A of uniform-pressure-drop valve 5, the oil inlet P of 3-position-3-way solenoid directional control valve 1 and 3-position-3-way electromagnetism
The oil inlet P of reversal valve 2 3.2 is connected by fluid pressure line, the oil return inlet T of 3-position-3-way solenoid directional control valve 1, three three
The oil return inlet T of electric change valve 2 3.2 and the first oil return inlet T 1, the second oil return inlet T 2 of integrated valve block 7 pass through fluid pressure line
It is connected, the actuator port A of 3-position-3-way solenoid directional control valve 1, the actuator port A of two-position two-way electromagnetic directional valve 6, two three
First actuator port A of the oil inlet P of electric change valve 2 2.2, the oil inlet P of secondary relief 1 and integrated valve block 7
It is connected by fluid pressure line, the oil inlet of the actuator port A, two-position two-way electromagnetic directional valve 6 of 3-position-3-way solenoid directional control valve 2 3.2
Mouthful P, the oil return inlet T of two position, three-way electromagnetic change valve 2 2.2, the oil inlet P of secondary relief 2 1.2 and integrated valve block 7 the
Two actuator port B are connected by fluid pressure line, the work of the actuator port A, secondary relief 2 1.2 of secondary relief 1
The first oil return inlet T 1, the second oil return inlet T 2 of hydraulic fluid port A, the oil inlet P of two position, three-way electromagnetic change valve 1 and integrated valve block 7
It is connected by fluid pressure line, oil return inlet T and the two position, three-way electromagnetic change valve 2 2.2 of two position, three-way electromagnetic change valve 1
Actuator port A is connected by fluid pressure line, and the actuator port A of two position, three-way electromagnetic change valve 1, the first of shuttle valve 4 are compared
Hydraulic fluid port A is connected with the control port X of uniform-pressure-drop valve 5 by fluid pressure line, and the of the output oil port C of shuttle valve 4 and integrated valve block 7
One load-sensitive hydraulic fluid port LS1 is connected by fluid pressure line, and the second of shuttle valve 4 compares minus second load of hydraulic fluid port B and integrated valve block 7
Sensitive hydraulic fluid port LS2 is connected by fluid pressure line.
The working principle of double valve-regulated load port separate control valves based on the compensation of machine hydraulic pressure difference: hydraulic oil passes through pile-up valve
The first oil inlet P 1 or the second oil inlet P 2 of block 7, after flowing through uniform-pressure-drop valve 5, are divided into two branches, flow into three three all the way
Electric change valve 1 flows into 3-position-3-way solenoid directional control valve 2 3.2,3-position-3-way solenoid directional control valve 1 and three all the way
Position three-way solenoid valve 2 3.2 can control the on-off of oil circuit and the size of flow by controlling input electrical signal, when three
When the spool of three-way solenoid valve 1 commutates to left position, the spool of 3-position-3-way solenoid directional control valve 2 3.2 then needs to commutate to
When right position, to realize one 3.1 oil inlet of 3-position-3-way solenoid directional control valve, high pressure is inputted to the first actuator port A of integrated valve block 7
Oil after hydraulic oil is backed into from the second actuator port B of integrated valve block 7, flows into integrated by 3-position-3-way solenoid directional control valve 1
The first oil return inlet T 1 or the second oil return inlet T 2 of valve block 7, when the spool of 3-position-3-way solenoid directional control valve 1 commutates to left position
When, then just on the contrary, 3-position-3-way solenoid directional control valve 1, which may be implemented, controls oil inlet, 3-position-3-way solenoid directional control valve 1
Oil return is controlled, the in-line of hydraulic actuator and the independent control of vent line may be implemented in whole process.When 3-position-3-way electromagnetism
Reversal valve 1 controls oil inlet, and when 3-position-3-way solenoid directional control valve 1 controls oil return, high pressure oil port is the of integrated valve block 7
One actuator port A, two position, three-way electromagnetic change valve 1 are in right position, and two position, three-way electromagnetic change valve 1 is in right position,
The operating pressure of first actuator port A of integrated valve block 7 can be introduced uniform-pressure-drop valve 5 control port X and shuttle valve 4 the
One compares hydraulic fluid port A, thus guaranteed by uniform-pressure-drop valve 5 inlet valve 3-position-3-way solenoid directional control valve 1 into and out of hydraulic fluid port
The pressure difference at both ends is steady state value, so that the flow for realizing that 3-position-3-way solenoid directional control valve 1 controls is unrelated with load, and by work
Make pressure to export by the output oil port C of shuttle valve 4 to the first load-sensitive hydraulic fluid port LS1 of integrated valve block 7；When 3-position-3-way electromagnetism
Reversal valve 1 controls oil inlet, and when 3-position-3-way solenoid directional control valve 1 controls oil return, high pressure oil port is the of integrated valve block 7
Two actuator port B, two position, three-way electromagnetic change valve 1 are in left position, and two position, three-way electromagnetic change valve 1 is in right position,
The operating pressure of second actuator port B of integrated valve block 7 can be introduced uniform-pressure-drop valve 5 control port X and shuttle valve 4 the
One compares hydraulic fluid port A, thus guaranteed by uniform-pressure-drop valve 5 inlet valve 3-position-3-way solenoid directional control valve 1 into and out of hydraulic fluid port
Both ends pressure difference is steady state value, so that the flow for realizing that 3-position-3-way solenoid directional control valve 1 controls is unrelated with load, and by work
Pressure is exported by the output oil port C of shuttle valve 4 to the first load-sensitive hydraulic fluid port LS1 of integrated valve block 7.
Further, the structure of secondary relief 2 1.2 is consistent with the structure of secondary relief 1, and principle is identical, this
It is referred to as secondary relief in section, as shown in Fig. 2, the secondary relief includes check valve 101 and overflow valve 102, check valve 101
Oil outlet A1 and the oil outlet A2 of overflow valve 102 the actuator port A of secondary relief is connected to form by fluid pressure line, unidirectionally
The oil inlet P 1 of valve 101 and the oil inlet P 2 of overflow valve 102 are connected to form the oil inlet P of secondary relief by fluid pressure line,
The oil inlet P of secondary relief is connected with the first actuator port A of actuator or the second actuator port B, actuator port A and oil return
Mouth T-phase connects, and when hydraulic oil is from oil inlet P oil inlet, oil outlet A oil return, hydraulic oil cannot pass through check valve 101, only reach
It after the setup pressure value of overflow valve 102, can just be flowed out from A mouthfuls, thus high pressure kicks can be played the role of；When hydraulic oil is from fuel-displaced
When mouthful A oil inlet, oil outlet P oil return, hydraulic oil passes through check valve 101, and without overflow valve 102, thus, when actuator is emptied
When, repairing can be played the role of.
The application also provides a kind of the hydraulic of double valve-regulated load port separate control valves that application is compensated based on machine hydraulic pressure difference
System, as shown in figure 3, including hydraulic cylinder 8, the first separate control valves 9, fuel tank 10, variable pump 11,12 and of the second separate control valves
Hydraulic motor 13, the second oil return inlet T 2 of the first separate control valves 9 pass through with the first oil return inlet T 1 of the second separate control valves 12
Fluid pressure line is connected, and forms common oil return opening, the second oil inlet P 2 of the first separate control valves 9 and the second separate control valves 12
First oil inlet P 1 is connected by fluid pressure line, forms common oil inlet, the second load-sensitive hydraulic fluid port of the first separate control valves 9
LS2 is connected with the first load-sensitive hydraulic fluid port LS1 of the second separate control valves 12 by fluid pressure line, and the sensitive oil of mutual load is formed
Mouthful, the inlet port T of variable pump 11 is connected with fuel tank 10 by fluid pressure line, the oil outlet P and the first independent control of variable pump 11
First oil inlet P 1 of valve 9 is connected by fluid pressure line, the load-sensitive hydraulic fluid port LS of variable pump 11 and the first separate control valves 9
First load-sensitive hydraulic fluid port LS1 is connected by fluid pressure line, and the second oil return inlet T 2 of the second separate control valves 12 passes through hydraulic tube
Road is connected with fuel tank 10, and the first oil return inlet T 1 of the first separate control valves 9, the second load-sensitive of the second separate control valves 12 are oily
Mouthful LS2, the second separate control valves 12 the second oil inlet P 2 blocked by plug, the first working oil of the first separate control valves 9
Mouthful A is connected with the first actuator port A of hydraulic cylinder 8 by fluid pressure line, the second actuator port B of the first separate control valves 9 and
Second actuator port B of hydraulic cylinder 8 by fluid pressure line be connected, the first actuator port A of the second separate control valves 12 with it is hydraulic
First actuator port A of motor 13 is connected by fluid pressure line, the second actuator port B of the second separate control valves 12 and hydraulic horse
The second actuator port B up to 13 is connected by fluid pressure line.
Using the working principle of the hydraulic system of the double valve-regulated load port separate control valves compensated based on machine hydraulic pressure difference: becoming
Amount pump 11 sucks hydraulic oil under the drive of motor or engine, from fuel tank 10, and only to the first separate control valves 9 and second
Vertical control valve 12 carries out fuel feeding, and the piston rod that the first separate control valves 9 control hydraulic cylinder 8 stretches out speed and direction, and second solely
Vertical control valve 12 controls rotary speed and the direction of hydraulic motor 13, and can be by hydraulic cylinder 8 and hydraulic motor 13 most
High operating pressure leads back the load-sensitive mouth LS of variable pump 11 by the first load-sensitive mouth LS1 of the first separate control valves 9, from
And while completing hydraulic actuator load port independent control, realize load-sensitive function.
Preferably, as shown in figure 4, double valve-regulated load port separate control valves based on the compensation of machine hydraulic pressure difference can be according to liquid
The quantity of pressure actuator is increase accordingly, and issues electric signal to each separate control valves using controller, to realize every
Control of one separate control valves to hydraulic actuator, for first, its working principle is that when controller experience it is automatically controlled
After the active input of handle, according to the size and Orientation of input signal, according to corresponding control logic, into first
Five solenoid valves issue automatically controlled signal, and then control the flow of disengaging, outflow hydraulic cylinder, realize one hydraulic actuator of control
Motion control.
It although an embodiment of the present invention has been shown and described, for the ordinary skill in the art, can be with
A variety of variations, modification, replacement can be carried out to these embodiments without departing from the principles and spirit of the present invention by understanding
And modification, the scope of the present invention is defined by the appended.
Claims (4)
1. a kind of double valve-regulated load port separate control valves based on the compensation of machine hydraulic pressure difference, it is characterised in that: including secondary overflow
First and second overflow valve two of valve, two position, three-way electromagnetic change valve one, two position, three-way electromagnetic change valve two, 3-position-3-way electromagnetic switch
Valve one, 3-position-3-way solenoid directional control valve two, shuttle valve, uniform-pressure-drop valve, two-position two-way electromagnetic directional valve and integrated valve block；
Be drilled on the integrated valve block the first oil inlet, the second oil inlet, the first oil return opening, the second oil return opening, first load it is quick
Feel hydraulic fluid port, the second load-sensitive hydraulic fluid port, the first actuator port and the second actuator port, first oil inlet and the second oil inlet
Connection, first oil return opening and the connection of the second oil return opening；
The oil inlet of the uniform-pressure-drop valve is connected with the first oil inlet of integrated valve block, the second oil inlet by fluid pressure line,
The actuator port of the uniform-pressure-drop valve, the oil inlet of 3-position-3-way solenoid directional control valve one and 3-position-3-way solenoid directional control valve two
Oil inlet is connected by fluid pressure line, time of the oil return opening, 3-position-3-way solenoid directional control valve two of 3-position-3-way solenoid directional control valve one
Hydraulic fluid port is connected with the first oil return opening of integrated valve block, the second oil return opening by fluid pressure line, 3-position-3-way solenoid directional control valve one
Actuator port, the actuator port of two-position two-way electromagnetic directional valve, the oil inlet of two position, three-way electromagnetic change valve two, secondary relief
One oil inlet is connected with the first actuator port of integrated valve block by fluid pressure line, the work of 3-position-3-way solenoid directional control valve two
Hydraulic fluid port, the oil inlet of two-position two-way electromagnetic directional valve, the oil return opening of two position, three-way electromagnetic change valve two, secondary relief two into
Hydraulic fluid port is connected with the second actuator port of integrated valve block by fluid pressure line, the actuator port of secondary relief one, secondary overflow
The actuator port of valve two, the first oil return opening of the oil inlet of two position, three-way electromagnetic change valve one and integrated valve block, the second oil return opening
It is connected by fluid pressure line, the oil return opening of two position, three-way electromagnetic change valve one and the actuator port of two position, three-way electromagnetic change valve two
It is connected by fluid pressure line, the actuator port of two position, three-way electromagnetic change valve one, the first of shuttle valve compare hydraulic fluid port and determine subtractive pressure
The control port of valve is connected by fluid pressure line, and the output oil port of shuttle valve and the first load-sensitive hydraulic fluid port of integrated valve block pass through liquid
Pressure pipe road is connected, and the second of shuttle valve compares hydraulic fluid port and be connected with the minus second load-sensitive hydraulic fluid port of integrated valve block by fluid pressure line.
2. a kind of double valve-regulated load port separate control valves based on the compensation of machine hydraulic pressure difference according to claim 1, special
Sign is: the secondary relief one includes check valve and overflow valve, the oil outlet of the check valve and the oil outlet of overflow valve
The actuator port of secondary relief one, the oil inlet of the check valve and the oil inlet of overflow valve are connected to form by fluid pressure line
The oil inlet of secondary relief one is connected to form by fluid pressure line.
3. a kind of double valve-regulated load port separate control valves based on the compensation of machine hydraulic pressure difference according to claim 1, special
Sign is: the structure of the secondary relief two is consistent with the structure of secondary relief one.
4. a kind of using the hydraulic of double valve-regulated load port separate control valves described in claim 1 based on the compensation of machine hydraulic pressure difference
System, it is characterised in that: including hydraulic cylinder, the first separate control valves, fuel tank, variable pump, the second separate control valves and hydraulic horse
It reaches, the second oil return opening of first separate control valves passes through fluid pressure line phase with the first oil return opening of the second separate control valves
Even, common oil return opening is formed, the second oil inlet of the first separate control valves passes through with the first oil inlet of the second separate control valves
Fluid pressure line is connected, and forms common oil inlet, the second load-sensitive hydraulic fluid port of the first separate control valves and the second separate control valves
The first load-sensitive hydraulic fluid port by fluid pressure line be connected, formed mutual load sensitivity hydraulic fluid port, the inlet port and fuel tank of variable pump
It is connected by fluid pressure line, the oil outlet of variable pump is connected with the first oil inlet of the first separate control valves by fluid pressure line,
The load-sensitive hydraulic fluid port of variable pump is connected with the first load-sensitive hydraulic fluid port of the first separate control valves by fluid pressure line, and second solely
Second oil return opening of vertical control valve is connected by fluid pressure line with fuel tank, and the first oil return opening of the first separate control valves, second are solely
Second load-sensitive hydraulic fluid port of vertical control valve, the second oil inlet of the second separate control valves are blocked by plug, the first independent control
First actuator port of valve processed is connected with the first actuator port of hydraulic cylinder by fluid pressure line, and the second of the first separate control valves
Actuator port is connected with the second actuator port of hydraulic cylinder by fluid pressure line, the first actuator port of the second separate control valves with
First actuator port of hydraulic motor is connected by fluid pressure line, the second actuator port and hydraulic motor of the second separate control valves
The second actuator port by fluid pressure line be connected.
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| CN201810964378.1A CN109139598A (en) | 2018-08-23 | 2018-08-23 | A kind of double valve-regulated load port separate control valves based on the compensation of machine hydraulic pressure difference |
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| CN201810964378.1A CN109139598A (en) | 2018-08-23 | 2018-08-23 | A kind of double valve-regulated load port separate control valves based on the compensation of machine hydraulic pressure difference |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111043091A (en) * | 2019-10-30 | 2020-04-21 | 润琛液压机械南通有限公司 | Control valve set of mower |
| CN111483284A (en) * | 2020-06-01 | 2020-08-04 | 苏州海科智能装备技术有限公司 | Hydraulic suspension system, lifting control method and multi-axis flat car |
| CN111594069A (en) * | 2020-05-19 | 2020-08-28 | 江苏理工学院 | Turnover type elevator control method based on load port independent control |
| CN113202833A (en) * | 2021-05-24 | 2021-08-03 | 华东交通大学 | Load port independent control system matched with electro-hydraulic flow |
| CN113915185A (en) * | 2021-09-28 | 2022-01-11 | 中联重科股份有限公司 | Load port independent control load sensitive multi-way valve and hydraulic system |
| CN116164003A (en) * | 2023-03-07 | 2023-05-26 | 浙江大学 | Load port independent control valve for distributed hydraulic system and control method thereof |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2939327A1 (en) * | 1979-09-28 | 1981-04-16 | G.L. Rexroth Gmbh, 8770 Lohr | Control block for several hydraulic consumer appliances - has restrictor incorporated in control slide of multiway valves |
| DE3825726A1 (en) * | 1988-07-28 | 1990-02-01 | Linde Ag | HYDRAULIC SHIFTING ARRANGEMENT FOR A VEHICLE WITH A HYDROSTATIC TRANSMISSION |
| CN104196800A (en) * | 2014-09-04 | 2014-12-10 | 燕山大学 | Combination valve with load sensitive function and capable of controlling inlet and outlet oil ways independently |
| CN104481953A (en) * | 2014-12-12 | 2015-04-01 | 燕山大学 | Integrated valve with flow distribution being irrelevant to load pressure and throttling edge being controlled independently |
-
2018
- 2018-08-23 CN CN201810964378.1A patent/CN109139598A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2939327A1 (en) * | 1979-09-28 | 1981-04-16 | G.L. Rexroth Gmbh, 8770 Lohr | Control block for several hydraulic consumer appliances - has restrictor incorporated in control slide of multiway valves |
| DE3825726A1 (en) * | 1988-07-28 | 1990-02-01 | Linde Ag | HYDRAULIC SHIFTING ARRANGEMENT FOR A VEHICLE WITH A HYDROSTATIC TRANSMISSION |
| CN104196800A (en) * | 2014-09-04 | 2014-12-10 | 燕山大学 | Combination valve with load sensitive function and capable of controlling inlet and outlet oil ways independently |
| CN104481953A (en) * | 2014-12-12 | 2015-04-01 | 燕山大学 | Integrated valve with flow distribution being irrelevant to load pressure and throttling edge being controlled independently |
Non-Patent Citations (2)
| Title |
|---|
| 刘凯磊: "挖掘机电液控制***进出口独立控制特性分析与实验研究", 《中国博士学位论文全文数据库工程科技II辑》 * |
| 沈树盛: "《汽车仪表、ABS、自动变速***疑难杂症》", 31 January 2004, 四川科学技术出版社 * |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111043091A (en) * | 2019-10-30 | 2020-04-21 | 润琛液压机械南通有限公司 | Control valve set of mower |
| CN111594069A (en) * | 2020-05-19 | 2020-08-28 | 江苏理工学院 | Turnover type elevator control method based on load port independent control |
| CN111594069B (en) * | 2020-05-19 | 2021-08-24 | 江苏理工学院 | Turnover type elevator control method based on load port independent control |
| CN111483284A (en) * | 2020-06-01 | 2020-08-04 | 苏州海科智能装备技术有限公司 | Hydraulic suspension system, lifting control method and multi-axis flat car |
| CN111483284B (en) * | 2020-06-01 | 2024-05-03 | 苏州海科智能装备技术有限公司 | Hydraulic suspension system, lifting control method and multi-axis flat car |
| CN113202833A (en) * | 2021-05-24 | 2021-08-03 | 华东交通大学 | Load port independent control system matched with electro-hydraulic flow |
| CN113202833B (en) * | 2021-05-24 | 2023-02-24 | 华东交通大学 | Load port independent control system matched with electro-hydraulic flow |
| CN113915185A (en) * | 2021-09-28 | 2022-01-11 | 中联重科股份有限公司 | Load port independent control load sensitive multi-way valve and hydraulic system |
| CN113915185B (en) * | 2021-09-28 | 2023-11-28 | 常德中联重科液压有限公司 | Load port independent control load sensitive multi-way valve and hydraulic system |
| CN116164003A (en) * | 2023-03-07 | 2023-05-26 | 浙江大学 | Load port independent control valve for distributed hydraulic system and control method thereof |
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Application publication date: 20190104 |