CN108317117B - Double-margin servo control valve group with low throttle noise - Google Patents
Double-margin servo control valve group with low throttle noise Download PDFInfo
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- CN108317117B CN108317117B CN201810284178.1A CN201810284178A CN108317117B CN 108317117 B CN108317117 B CN 108317117B CN 201810284178 A CN201810284178 A CN 201810284178A CN 108317117 B CN108317117 B CN 108317117B
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- 238000006073 displacement reaction Methods 0.000 claims abstract description 28
- 230000001502 supplementing effect Effects 0.000 claims description 15
- 239000012530 fluid Substances 0.000 claims description 8
- 239000003792 electrolyte Substances 0.000 claims description 3
- 230000009977 dual effect Effects 0.000 claims 2
- 238000005265 energy consumption Methods 0.000 abstract description 2
- 230000010354 integration Effects 0.000 abstract description 2
- 239000007788 liquid Substances 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 230000006978 adaptation Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
Classifications
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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
- F15B13/025—Pressure reducing 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
- 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
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- 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)
- Servomotors (AREA)
Abstract
The invention belongs to the field of hydraulic servo control systems, and provides a double-margin servo control valve bank with low throttling noise. According to the invention, through the combination integration of the three-position three-way hydraulic reversing valve, the two-position two-way electro-hydraulic reversing valve, the one-way valve, the two-position six-way electro-hydraulic reversing valve and other hydraulic elements, the redundant backup of the servo valve is realized, the load self-adaptive change of the P port pressure of the servo valve is realized, the steering engine displacement closed-loop control of a larger overrun load can be realized by lower oil supply pressure, the pressure difference of the valve port of the servo valve under the overrun load condition is reduced, the throttling noise of the control valve group is reduced, and the energy consumption is reduced.
Description
Technical Field
The invention belongs to the field of hydraulic servo control systems, and particularly relates to a double-margin servo control valve group with low throttle noise.
Background
The servo control valve group generally comprises a servo valve and other auxiliary hydraulic elements, and is mainly used for controlling a hydraulic servo steering engine system to realize displacement closed loop of a steering engine hydraulic cylinder.
The current servo control valve group takes a constant pressure source as a power source, and under the action of a larger overrun load (the direction of the load of the hydraulic cylinder is the same as the movement direction of the hydraulic cylinder), the pressure difference at two ends of a valve port of the servo valve in the control valve group is very large, so that throttling noise is larger. In addition, under the condition of smaller load, the pressure of the constant pressure source can be much higher than the load, and when the steering engine hydraulic cylinder is controlled in a closed loop, the pressure difference at two ends of a valve port of the servo valve is also large, and meanwhile, the energy loss is also large.
Disclosure of Invention
The invention aims to overcome the defects in the prior art, and provides the double-margin servo control valve group with low throttling noise, which can effectively improve the reliability of the control valve group. When the load is large, the servo valve pressure oil port selects a high-pressure source as a power source, and when the load is low or the load exceeds the load, the servo valve pressure oil port selects a low-pressure source as the power source, so that the pressure difference of a valve port is reduced, throttling noise is reduced, and meanwhile, energy loss is also reduced.
The technical scheme adopted for solving the technical problems is as follows: a double-margin servo control valve group with low throttle noise comprises a three-position three-way hydraulic reversing valve, a two-position two-way electro-hydraulic reversing valve, a first one-way valve, a main servo valve, an oil supplementing one-way valve, a control module and a throttle valve;
the three-position three-way hydraulic reversing valve is provided with valve core displacement feedback, P, T ports of the three-position three-way hydraulic reversing valve are communicated with a high-pressure oil source, A ports of the three-position three-way hydraulic reversing valve are communicated with P ports of two-position two-way electro-hydraulic reversing valves, and hydraulic control ports of the three-position three-way hydraulic reversing valve are respectively connected with A, B ports of a hydraulic cylinder;
the initial position of the two-position two-way electric fluid reversing valve is a conducting position, and an A port of the two-position two-way electric fluid reversing valve is communicated with a P port of the main servo valve; the two-position two-way electrolyte reversing valve realizes reversing under the action of a control signal;
the main servo valve is provided with valve core displacement feedback, the P port of the main servo valve is communicated with a low-pressure oil source through a first one-way valve, the A, B port of the main servo valve is connected with the A, B port of the hydraulic cylinder, and the T port of the main servo valve is connected with the throttle valve; the main servo valve realizes displacement closed-loop control of the hydraulic cylinder under the action of a control signal, and feeds back a valve core displacement signal;
the number of the oil supplementing one-way valves is 2, the B ports of the oil supplementing one-way valves are respectively connected with the A, B ports of the main servo valve, and the A ports of the oil supplementing one-way valves are connected with the T ports of the main servo valve; the oil supplementing one-way valve has the function of supplementing oil to the opening A, B of the servo valve under the working condition of exceeding load.
The control module comprises a power supply, a CPU, an analog input/output module and an I/0 module, wherein the analog input/output module is connected with a main servo valve core, a standby servo valve core and a three-position three-way hydraulic reversing valve core, the I/0 module is connected with a two-position two-way electro-hydraulic reversing valve, the control module judges whether a load is exceeded or not by collecting displacement feedback signals of the main servo valve core and the three-position three-way hydraulic reversing valve core, and further controls the power-on or power-off of the two-position two-way electro-hydraulic reversing valve;
one end of the throttle valve is connected with the T port of the main servo valve, and the other end of the throttle valve is connected with the oil tank, so that the servo valve T port generates certain back pressure, multi-stage throttling is realized, and throttling noise is reduced.
The first one-way valve and the second one-way valve have the function of realizing one-way isolation of the high-pressure oil source and the low-pressure oil source.
The double-margin servo control valve group with low throttle noise further comprises a standby servo valve and a two-position six-way electric liquid reversing valve, wherein the standby servo valve is identical in structure with the main servo valve, a P port of the standby servo valve is communicated with a P port of the main servo valve through a second one-way valve, and meanwhile, the P port of the standby servo valve is communicated with a P port of the two-position two-way electric liquid reversing valve and an A port of the three-position three-way hydraulic reversing valve, and a T port of the standby servo valve is communicated with a T port of the main servo valve; the pressure oil port and the oil return port of the two-position six-way hydraulic reversing valve are respectively communicated with A, B ports of the main servo valve and the standby servo valve, and A, B ports of the two-position six-way hydraulic reversing valve are connected with A, B ports of the hydraulic cylinder.
In the technical scheme, the main servo valve, the standby servo valve and the two-position six-way electro-hydraulic reversing valve complete redundant backup of the servo valve, and the two-position six-way electro-hydraulic reversing valve complete switching of oil paths of the main servo valve and the standby servo valve through reversing.
In the technical scheme, the three-position three-way hydraulic reversing valve is a reversing valve with a symmetrical structure function, namely the valve core has the same function after moving leftwards and rightwards. When the three-position three-way hydraulic reversing valve is in the middle position, the reversing valve is in the stop position; when the valve core is opened to a certain extent (the load is larger than a certain value, the value can be set through parameter design), the reversing valve is in a conducting state, and the smoothness of the oil supply path from the high-pressure oil source to the servo valve is realized.
The invention provides a double-margin servo control valve group with low throttling noise, which utilizes a three-position three-way hydraulic reversing valve and a two-position two-way electro-hydraulic reversing valve to realize the load self-adaptation of the P port pressure of a main servo valve and the function of switching the P port pressure of the main servo valve to a low pressure oil source under the condition of exceeding the load. When the three-position three-way hydraulic reversing valve is in the neutral position in the initial state, the two-position two-way electro-hydraulic reversing valve is in the initial position, and when the main servo valve steers, under the condition of low positive load and low negative load, the load is insufficient to overcome the spring force of the three-position three-way hydraulic reversing valve to open the three-position three-way hydraulic reversing valve, and the pressure source of the P port of the main servo valve is provided by a low-pressure oil source. Under the condition of exceeding a load, the two-position two-way electric liquid reversing valve is powered, and the pressure of the P port of the main servo valve is provided by a low-pressure oil source no matter how large the absolute value of the load is. Under the condition of larger positive load, the load overcomes the spring force of the three-position three-way hydraulic reversing valve to open the three-position three-way hydraulic reversing valve, the pressure source of the P port of the main servo valve is provided by a high-pressure oil source, meanwhile, as the load is increased, the valve core opening of the three-position three-way hydraulic reversing valve is increased, the smaller the throttling loss of the high-pressure oil source through the valve is, the larger the pressure of the P port of the main servo valve is, and the load change is adapted.
The P port of the servo valve is directly communicated with the A port of the three-position three-way hydraulic reversing valve, so that the pressure adaptation of the P port of the servo valve to the load change can be realized, namely, when the load is large, the P port oil supply pressure is large, the load is low, and the P port oil supply pressure is low.
The invention has the advantages that the redundant backup of the servo valve is realized through the combination and integration of the hydraulic elements such as the three-position three-way hydraulic reversing valve, the two-position two-way electro-hydraulic reversing valve, the one-way valve, the two-position six-way electro-hydraulic reversing valve and the like, the load self-adaptive change of the pressure at the P port of the servo valve is realized, the steering engine displacement closed-loop control of a larger overrun load can be realized through lower oil supply pressure, the pressure difference of the valve port of the servo valve under the overrun load condition is reduced, the throttling noise of the control valve group is reduced, and the energy consumption is reduced.
Drawings
Fig. 1 is a schematic diagram of an embodiment of the present invention.
In the figure: the hydraulic valve comprises a three-position three-way hydraulic reversing valve 1, a two-position two-way electro-hydraulic reversing valve 2, a second one-way valve 3, a main servo valve 4, a standby servo valve 5, a two-position six-way electro-hydraulic reversing valve 6, an oil supplementing one-way valve 7, a control module 8, a throttle valve 9 and a first one-way valve 10.
Fig. 2 is a schematic diagram of an initial state structure of a three-position three-way hydraulic reversing valve in an embodiment.
Fig. 3 is a schematic diagram of a critical opening state structure when the valve core of the three-position three-way hydraulic reversing valve moves rightward in the embodiment.
Fig. 4 is a schematic diagram of a three-position three-way hydraulic reversing valve in a fully opened state.
Detailed Description
The invention is further described below with reference to the accompanying drawings.
As shown in fig. 1, the embodiment of the invention provides a low-throttle-noise double-margin servo control valve group, which comprises a three-position three-way hydraulic reversing valve 1, a two-position two-way electro-hydraulic reversing valve 2, a second one-way valve 3, a main servo valve 4, a standby servo valve 5, a two-position six-way electro-hydraulic reversing valve 6, an oil supplementing one-way valve 7, a control module 8, a throttle valve 9 and a first one-way valve 10.
The three-position three-way hydraulic reversing valve 1 is provided with valve core displacement feedback, the P, T ports of the three-position three-way hydraulic reversing valve 1 are all communicated with a high-pressure oil source, the A port of the three-position three-way hydraulic reversing valve 1 is communicated with the P port of the two-position two-way electro-hydraulic reversing valve 2, and the hydraulic control ports of the three-position three-way hydraulic reversing valve 1 are respectively connected with the A, B ports of the hydraulic cylinder;
the initial position of the two-position two-way electric fluid reversing valve 2 is a conducting position, and an A port of the two-position two-way electric fluid reversing valve 2 is communicated with a P port of the main servo valve 4; the two-position two-way electrolyte reversing valve 2 realizes reversing under the action of a control signal;
the main servo valve 4 is provided with valve core displacement feedback, a P port of the main servo valve 4 is communicated with a low-pressure oil source through a first one-way valve 10, a A, B port of the main servo valve 4 is communicated with the two six-position electrified liquid reversing valve 6, and a T port of the main servo valve 4 is connected with a throttle valve; the main servo valve 4 realizes displacement closed-loop control of the hydraulic cylinder under the action of a control signal, and feeds back a valve core displacement signal;
the structure of the standby servo valve 5 is the same as that of the main servo valve 4, the P port of the standby servo valve 5 is communicated with the P port of the main servo valve 4 through the second one-way valve 3, meanwhile, the P port of the standby servo valve 5 is communicated with the P port of the two-position two-way electro-hydraulic reversing valve 2 and the A port of the three-position three-way hydraulic reversing valve 1, and the T port is communicated with the T port of the main servo valve 4;
the pressure oil port and the oil return port of the two-position six-way fluid reversing valve 6 are respectively communicated with A, B ports of the main servo valve and the standby servo valve, and A, B ports of the two-position six-way fluid reversing valve 6 are connected with A, B ports of the hydraulic cylinder;
the number of the oil supplementing one-way valves 7 is 2, the ports B of the oil supplementing one-way valves are respectively connected with A, B ports of the two-position six-way electric liquid reversing valve 6, and the ports A of the oil supplementing one-way valves 7 are connected with the ports T of the main servo valve and the standby servo valve;
the control module comprises a power supply, a CPU, an analog input/output module and an I/0 module, wherein the analog input/output module is connected with a main servo valve core, a standby servo valve core and a three-position three-way hydraulic reversing valve core, the I/0 module is connected with a two-position two-way electro-hydraulic reversing valve, the control module judges whether a load is exceeded or not by collecting displacement feedback signals of the main servo valve core, the standby servo valve core and the three-position three-way hydraulic reversing valve core, and further controls the power-on or power-off of the two-position two-way electro-hydraulic reversing valve;
one end of the throttle valve is connected with the T-shaped ports of the main servo valve and the standby servo valve, and the other end of the throttle valve is connected with the oil tank.
For the convenience of explanation of the working principle, the following definitions are made:
a) The pressure of two cavities of the hydraulic cylinder is represented by Pa and Pb respectively, and the load pressure Pf=Pa-Pb;
b) The valve core displacement of the three-position three-way hydraulic reversing valve is represented by x, the valve core displacement of the servo valve is represented by z, and the right direction of the displacement of the valve core and the hydraulic cylinder is positive, and the left direction is negative.
The working principle of the double-margin servo control valve group with low throttle noise comprises two major parts, namely a redundant backup of a servo valve and a low throttle noise principle.
a) Redundant backup of servo valves
In the initial state, the A, B port of the main servo valve 4 is communicated with the A, B port of the hydraulic cylinder, the A, B port of the standby servo valve 5 is cut off, and the main servo valve 4 controls the hydraulic cylinder; when the two-position six-way electric liquid reversing valve 6 is powered on, the A, B port of the standby servo valve 5 is communicated with the A, B port of the hydraulic cylinder, the A, B port of the main servo valve 4 is cut off, and the standby servo valve 5 controls the hydraulic cylinder.
b) Low throttle noise working principle
1) Pa is greater than Pb, and the hydraulic cylinder moves rightwards (positive load condition)
When Pa is larger than Pb and the hydraulic cylinder moves rightwards (for example, the hydraulic cylinder moves rightwards from zero position and overcomes the load to do work), the valve core of the three-position three-way hydraulic reversing valve 1 moves rightwards under the action of pressure difference between Pa and Pb, the valve core displacement x of the three-position three-way hydraulic reversing valve 1 collected by the control module 8 is positive, the valve core displacement z of the main servo valve 4 is negative, and at the moment, the control signal sent by the control module 8 to the two-position two-way electro-hydraulic reversing valve 2 is 0, namely power is lost.
If Pf (Pa-Pb) is smaller than the set value, the spool displacement of the three-position three-way hydraulic reversing valve 1 is not large enough (the spool position state shown in fig. 3), at this time, the high-pressure oil source PH still cannot pass through the orifice of the spool, at this time, the P port pressure of the main servo valve 4 is only communicated with the low-pressure oil source PL, that is, the P port pressure is low, at this time, the main servo valve 4 performs the valve control operation under the condition of supplying the oil from the low-pressure oil source.
When Pf is greater than the set value, the load pressure Pf is sufficient to overcome the spring force of the three-position three-way hydraulic reversing valve 1, so that the a and PH ports of the valve core are communicated (as shown in fig. 4), high-pressure oil at the PH port is supplied to the P port of the main servo valve 4 through the three-position three-way hydraulic reversing valve 1 and the two-position two-way electro-hydraulic reversing valve 2, meanwhile, due to the effect of the first one-way valve 10, the P port high-pressure oil cannot circulate to the PL port, in this case, the P port pressure of the main servo valve 4 is automatically switched to a high-pressure oil system, in addition, as the load pressure increases, the valve core opening amount of the three-position three-way hydraulic reversing valve 1 increases, the pressure loss of the valve core of the PH through the three-position three-way hydraulic reversing valve 1 decreases, and as the P port pressure of the main servo valve 4 gradually increases along with the load pressure, thereby playing a role of load self-adaption.
2) Pa is greater than Pb, and the cylinder moves to the left (overrunning load conditions)
a) When Pa is greater than Pb and the hydraulic cylinder moves leftwards (for example, the hydraulic cylinder moves from the maximum value of the right position to the zero position, and the load drives the hydraulic cylinder to move), the valve core of the three-position three-way hydraulic reversing valve 1 moves leftwards under the action of the pressures Pa and Pb, the valve core displacement x of the three-position three-way hydraulic reversing valve 1 collected by the control module 8 is positive, the valve core displacement z of the main servo valve 4 is positive, and at the moment, the control signal sent by the control module 8 to the two-position two-way electro-hydraulic reversing valve 2 is 1, namely, the two-position two-way electro-hydraulic reversing valve 2 is electrified.
b) If Pf is smaller than the set value, the spool displacement of the three-position three-way hydraulic reversing valve 1 is not large enough (the spool position state shown in fig. 3), at this time, the high-pressure oil source PH still cannot pass through the throttle orifice of the spool, at this time, the pressure of the port P of the servo valve is only communicated with the low-pressure oil source PL, that is, the pressure of the port P is low, and the main servo valve 4 performs the valve control operation under the condition of supplying oil to the low-pressure oil source.
c) When Pf is greater than the set value, the load pressure is greater at this time and is sufficient to overcome the spring force of the three-position three-way hydraulic reversing valve 1, so that the ports a and PH of the valve core are communicated (as shown in fig. 4), but at this time, the two-position two-way electro-hydraulic reversing valve 2 is at the left position, the high-pressure oil at port a cannot supply high-pressure oil to the port P of the main servo valve 4 through the two-position two-way electro-hydraulic reversing valve 2, in this case, the pressure at the port P of the main servo valve 4 is only communicated with the low-pressure oil source PL, i.e., the pressure at the port P is low, the main servo valve 4 performs the valve control operation under the condition of exceeding the load under the condition of supplying oil from the low-pressure oil source, and the pressure difference between the ports P and B of the main servo valve 4 is reduced.
3) Pb is greater than Pa
At this time, the working principle is the same as Pa is greater than Pb (because the left and right working positions of the three-position three-way hydraulic reversing valve 1 are the same), except that when Pa is greater than Pb, the three-position three-way hydraulic reversing valve 1 works at the left position, and when Pb is greater than Pa, the three-position three-way hydraulic reversing valve 1 works at the right position.
In summary, the above embodiments are only preferred embodiments of the present invention, and are not intended to limit the scope of the present invention. The scheme is just one of the examples of the patent, and the hydraulic reversing valve with the same function can still complete all the functions of the example by replacing the electromagnetic reversing valve with the same function. The invention not only can be used for closed-loop control of the displacement of the steering engine system, but also can be used for realizing closed-loop control of the position in other hydraulic servo systems.
What is not described in detail in this specification is prior art known to those skilled in the art.
Claims (3)
1. A low-throttle-noise double-margin servo control valve group is characterized in that: the hydraulic control system comprises a three-position three-way hydraulic reversing valve, a two-position two-way electro-hydraulic reversing valve, a first one-way valve, a main servo valve, an oil supplementing one-way valve, a control module and a throttle valve;
the three-position three-way hydraulic reversing valve is provided with valve core displacement feedback, P, T ports of the three-position three-way hydraulic reversing valve are all communicated with a high-pressure oil source, A ports of the three-position three-way hydraulic reversing valve are communicated with P ports of two-position two-way electro-hydraulic reversing valves, and hydraulic control ports of the three-position three-way hydraulic reversing valve are respectively connected with A, B ports of a hydraulic cylinder;
the initial position of the two-position two-way electric fluid reversing valve is a conducting position, and an A port of the two-position two-way electric fluid reversing valve is communicated with a P port of the main servo valve; the two-position two-way electrolyte reversing valve realizes reversing under the action of a control signal;
the main servo valve is provided with valve core displacement feedback, the P port of the main servo valve is communicated with a low-pressure oil source through a first one-way valve, the A, B port of the main servo valve is connected with the A, B port of the hydraulic cylinder, and the T port of the main servo valve is connected with the throttle valve; the main servo valve realizes displacement closed-loop control of the hydraulic cylinder under the action of a control signal, and feeds back a valve core displacement signal;
the number of the oil supplementing one-way valves is 2, the ports B of the oil supplementing one-way valves are respectively connected with the A, B ports of the main servo valves, and the ports A of the oil supplementing one-way valves are connected with the ports T of the main servo valves;
the control module is an electrical control module, judges whether to surpass a load by collecting displacement feedback signals of a valve core of the main servo valve and a valve core of the three-position three-way hydraulic reversing valve, further controls the power supply or power failure of the two-position two-way electro-hydraulic reversing valve, and when the load is surpassed, the two-position two-way electro-hydraulic reversing valve is powered on, otherwise the power is lost;
one end of the throttle valve is connected with the T-shaped port of the main servo valve, and the other end of the throttle valve is connected with the oil tank.
2. The low throttle noise dual margin servo control valve set of claim 1, wherein: the device comprises a standby servo valve and a two-position six-way electro-hydraulic reversing valve, wherein the standby servo valve has the same structure as the main servo valve, the P port of the standby servo valve is communicated with the P port of the main servo valve through a second one-way valve, and meanwhile, the P port of the standby servo valve is communicated with the P port of the two-position two-way electro-hydraulic reversing valve and the A port of the three-position three-way hydraulic reversing valve, and the T port of the standby servo valve is communicated with the T port of the main servo valve; the pressure oil port and the oil return port of the two-position six-way hydraulic reversing valve are respectively communicated with A, B ports of the main servo valve and the standby servo valve, and A, B ports of the two-position six-way hydraulic reversing valve are connected with A, B ports of the hydraulic cylinder.
3. The low throttle noise dual margin servo control valve set of claim 2, wherein: the control module comprises a power supply, a CPU, an analog input/output module and an I/0 module, wherein the analog input/output module is connected with a main servo valve core, a standby servo valve core and a three-position three-way hydraulic reversing valve core, and the I/0 module is connected with a two-position two-way electro-hydraulic reversing valve.
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Citations (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2645215A2 (en) * | 1987-10-05 | 1990-10-05 | Rexroth Mannesmann Gmbh | LOAD INDEPENDENT CONTROL DEVICE FOR HYDRAULIC USER DEVICES |
| JP2001027203A (en) * | 1999-07-12 | 2001-01-30 | Hitachi Constr Mach Co Ltd | Directional control valve device with hydraulic regenerative circuit |
| CN201078362Y (en) * | 2006-12-14 | 2008-06-25 | 天津市华泰森淼生物工程技术有限公司 | Hydraulic pressure control system of integration supervoltage biological treatment equipment |
| CN101532517A (en) * | 2009-04-10 | 2009-09-16 | 长春理工大学 | Method for simulating servo system load by electrohydraulic servo |
| CN202250059U (en) * | 2011-06-03 | 2012-05-30 | 中国船舶重工集团公司第七○五研究所高技术公司 | Pump suction-draining device for formation tester |
| CN102513413A (en) * | 2011-12-03 | 2012-06-27 | 南京埃尔法电液技术有限公司 | Hydraulic control system for novel servo pump control bending machine |
| CN103148041A (en) * | 2013-03-07 | 2013-06-12 | 北京理工大学 | Energy-saving active/passive load double electrohydraulic servo valve control system and control method thereof |
| CN104295551A (en) * | 2014-08-18 | 2015-01-21 | 中国农业大学 | Self-steering proportional control valve block and navigation hydraulic system based on self-steering proportional control valve block |
| CN104564885A (en) * | 2015-01-08 | 2015-04-29 | 宁波宇洲液压科技有限公司 | High-integration bidirectional rotary valve for pilot control mode |
| WO2015117338A1 (en) * | 2014-02-10 | 2015-08-13 | 太原理工大学 | Single-hydraulic motor double-loop control system |
| DE102015209074B3 (en) * | 2015-05-18 | 2016-08-25 | Danfoss Power Solutions Gmbh & Co. Ohg | DEVICE AND METHOD FOR CONTROLLING A HYDRAULIC MACHINE |
| EP3104022A1 (en) * | 2015-06-12 | 2016-12-14 | National Oilwell Varco Norway AS | Improvements in the control of hydraulic actuators |
| CA2955713A1 (en) * | 2015-10-27 | 2017-04-27 | China University Of Mining And Technology | A multi-cylinder synchronous energy-saving and efficient hydraulic lift system and method thereof |
| CN106939909A (en) * | 2017-05-10 | 2017-07-11 | 吉林大学 | A kind of hydraulic auxiliary driving system of integrated hydraulic starter |
| CN208138231U (en) * | 2018-04-02 | 2018-11-23 | 中国船舶重工集团公司第七一九研究所 | A kind of double nargin SERVO CONTROL valve groups of low throttling noise |
-
2018
- 2018-04-02 CN CN201810284178.1A patent/CN108317117B/en active Active
Patent Citations (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2645215A2 (en) * | 1987-10-05 | 1990-10-05 | Rexroth Mannesmann Gmbh | LOAD INDEPENDENT CONTROL DEVICE FOR HYDRAULIC USER DEVICES |
| JP2001027203A (en) * | 1999-07-12 | 2001-01-30 | Hitachi Constr Mach Co Ltd | Directional control valve device with hydraulic regenerative circuit |
| CN201078362Y (en) * | 2006-12-14 | 2008-06-25 | 天津市华泰森淼生物工程技术有限公司 | Hydraulic pressure control system of integration supervoltage biological treatment equipment |
| CN101532517A (en) * | 2009-04-10 | 2009-09-16 | 长春理工大学 | Method for simulating servo system load by electrohydraulic servo |
| CN202250059U (en) * | 2011-06-03 | 2012-05-30 | 中国船舶重工集团公司第七○五研究所高技术公司 | Pump suction-draining device for formation tester |
| CN102513413A (en) * | 2011-12-03 | 2012-06-27 | 南京埃尔法电液技术有限公司 | Hydraulic control system for novel servo pump control bending machine |
| CN103148041A (en) * | 2013-03-07 | 2013-06-12 | 北京理工大学 | Energy-saving active/passive load double electrohydraulic servo valve control system and control method thereof |
| WO2015117338A1 (en) * | 2014-02-10 | 2015-08-13 | 太原理工大学 | Single-hydraulic motor double-loop control system |
| CN104295551A (en) * | 2014-08-18 | 2015-01-21 | 中国农业大学 | Self-steering proportional control valve block and navigation hydraulic system based on self-steering proportional control valve block |
| CN104564885A (en) * | 2015-01-08 | 2015-04-29 | 宁波宇洲液压科技有限公司 | High-integration bidirectional rotary valve for pilot control mode |
| DE102015209074B3 (en) * | 2015-05-18 | 2016-08-25 | Danfoss Power Solutions Gmbh & Co. Ohg | DEVICE AND METHOD FOR CONTROLLING A HYDRAULIC MACHINE |
| EP3104022A1 (en) * | 2015-06-12 | 2016-12-14 | National Oilwell Varco Norway AS | Improvements in the control of hydraulic actuators |
| CA2955713A1 (en) * | 2015-10-27 | 2017-04-27 | China University Of Mining And Technology | A multi-cylinder synchronous energy-saving and efficient hydraulic lift system and method thereof |
| CN106939909A (en) * | 2017-05-10 | 2017-07-11 | 吉林大学 | A kind of hydraulic auxiliary driving system of integrated hydraulic starter |
| CN208138231U (en) * | 2018-04-02 | 2018-11-23 | 中国船舶重工集团公司第七一九研究所 | A kind of double nargin SERVO CONTROL valve groups of low throttling noise |
Non-Patent Citations (2)
| Title |
|---|
| 电液伺服阀的研究现状和发展趋势;陈彬,易孟林;液压与气动(06);全文 * |
| 电液伺服阀静态性能试验台;顾建,叶菊芳,吴彤;实验技术与管理(第02期);全文 * |
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