CN107461516A - A kind of differential type electric-hydraulic proportion uniform-pressure-drop valve - Google Patents
A kind of differential type electric-hydraulic proportion uniform-pressure-drop valve Download PDFInfo
- Publication number
- CN107461516A CN107461516A CN201710649136.9A CN201710649136A CN107461516A CN 107461516 A CN107461516 A CN 107461516A CN 201710649136 A CN201710649136 A CN 201710649136A CN 107461516 A CN107461516 A CN 107461516A
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- Prior art keywords
- valve
- pressure
- valve element
- hydraulic
- drop
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
- F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K27/00—Construction of housing; Use of materials therefor
- F16K27/04—Construction of housing; Use of materials therefor of sliding valves
- F16K27/041—Construction of housing; Use of materials therefor of sliding valves cylindrical slide valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/30—Details
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/30—Details
- F16K3/314—Forms or constructions of slides; Attachment of the slide to the spindle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0603—Multiple-way valves
- F16K31/061—Sliding valves
- F16K31/0613—Sliding valves with cylindrical slides
Abstract
The present invention relates to a kind of new construction of New Type of Differential dynamic formula electric-hydraulic proportion uniform-pressure-drop valve, the electric-hydraulic proportion uniform-pressure-drop valve includes：Valve element, have：Valve element connecting portion, positioned at valve element upper end, valve element top, middle part provide differential area, valve element bottom, positioned at valve element lower end；Valve pocket, wherein intake channel, the valve pocket, exit passageway or oil return opening passage form fluid passage；Proportion electro-magnet, there is provided electromagnetic force, ensure the electric-hydraulic proportion uniform-pressure-drop valve inlet outlet pressure differential with electric signal consecutive variations；Valve rod, the valve rod extend in the valve body and moved along the longitudinal axis of the valve rod, and the valve rod has first end and the second end；The present invention is simple in construction, and easy to maintain, the design of the pressure differential structure of the electric-hydraulic proportion uniform-pressure-drop valve effectively reduces the electromagnetic force of proportion electro-magnet, so as to reduce the volume of the volume of proportion electro-magnet and whole electric-hydraulic proportion uniform-pressure-drop valve.
Description
Technical field
The present invention relates to Hydraulic Elements, more particularly relate to a kind of new construction of differential type electric-hydraulic proportion uniform-pressure-drop valve.
Background technology
The continuous development of modern industry proposes in terms of automation, precision, response speed more and more high to hydraulic valve
It is required that traditional switching mode or setting control type hydraulic valve can not meet to require, therefore electrohydraulic servo valve grows up, and it has
Have the advantages that control is flexible, precision is high, rapidity is good, but electrohydraulic servo valve cost is high, application and maintenance condition are harsh, it is electro-hydraulic
Proportioning valve grows up on the basis of electro-hydraulic servo technology, and it has, and contamination resistance is strong, simple in construction, manufacture and safeguard into
Originally the advantage such as low compared with servo valve, therefore in hydraulic control system field using more and more extensive.
Hydraulic Field, often system bulk, weight are strict with, such as in aviation field, aircraft is to power-by-wire direction
Development, the problem of temperature rise that the fax hydrostatic actuator being related to solve constant displacement pump is brought, devises a kind of Stress control swash plate and inclines
The variable pump at angle, pressure is directly fed back to the problem of dynamic response difference during variable pump be present, to solve the problems, such as dynamic response, anti-
Feedthrough road adds electro-hydraulic proportional reducing valve and is used for improving dynamic property, now, the body of electric-hydraulic proportion uniform-pressure-drop valve valve body in itself
Product and weight will influence the weight of fax hydrostatic actuating system, so that influenceing the performance of aircraft.The mitigation of aircraft overall weight,
For passenger plane, help to save aircraft fuel oil, for fighter plane, its survival ability and reliability enhancing.
Hydraulic control system pressure is generally large, makes the pressure for acting on electro-hydraulic proportional reducing valve valve element larger, makes tradition
The electromagnetic force of the proportion electro-magnet of electro-hydraulic proportional reducing valve is too big, and its proportion electro-magnet volume is too big, adds whole hydraulic pressure system
The weight of system, in order to farthest reduce the weight of hydraulic control valve, there is an urgent need to a kind of new pressure-control valve.It is aobvious
So, this new electric-hydraulic proportion uniform-pressure-drop valve can effectively reduce actuator weight and and volume, have and important apply valency
Value.
The content of the invention
The purpose of the present invention be for hydraulic system pressure it is larger caused by decompression valve core equilibrant force is excessive and electromagnetic force
The bulky problem of proportion electro-magnet caused by excessive, propose that a kind of differential type electric-hydraulic proportion uniform-pressure-drop valve of new structure comes
Reduce valve element equilibrant force, so as to reduce electro-hydraulic proportional reducing valve volume.
The purpose of the present invention can be realized by following structure and technical principle：
The present invention is directed to the problem of electro-hydraulic proportional reducing valve proportion electro-magnet thrust is big, it is proposed that a kind of electro-hydraulic ratio of differential type
Example uniform-pressure-drop valve, can effectively reduce proportion electro-magnet thrust.Electric-hydraulic proportion uniform-pressure-drop valve includes：
Proportion electro-magnet, the proportion electro-magnet are the electromechanical conversion element of electric-hydraulic proportion uniform-pressure-drop valve, will be obtained
Electric signal converting to force signal, compared with hydraulic coupling control valve element restriction size, keep electric-hydraulic proportion uniform-pressure-drop valve enter
Pressure difference is exported with electric signal consecutive variations, proportion electro-magnet lower end convex shoulder is used to position；
Valve body, the valve body have a fluid import, fluid outlet and fluid oil return opening, fluid oil return opening and accumulator or
Fuel tank is connected, and valve body import outlet oil return opening difference thread mill drilling is connected with pipe joint, to ensure the company of pipe joint and valve body
Precision is connect, processes appropriately sized unthreaded hole, wherein coupling part planarity requirements are suitably strict, the processing of valve body upper end and ratio electricity
The unthreaded hole that magnet convex shoulder coordinates, ensure sealing with O-ring during cooperation；After side passageway machining, Outboard Sections hydraulic pressure plug
Block, ensure that return pressure guides to valve element upper end；
Wherein, when liquid stream flows through pressure-reducing valve, the size and Orientation of flow stream velocity changes, and its momentum change can be to valve element
Produce a hydraulic power, in order to reduce interference of the hydraulic power to valve element dynamic balance, the design compensation hydraulic power at valve body oil-out
Structure.
Valve pocket, the valve pocket form fluid passage, side by intake channel, valve pocket, exit passageway or oil return opening passage
Outlet pressure is guided to valve element upper end by passage；
Valve rod, the valve rod extend in valve body and moved along the longitudinal axis of valve rod；The valve rod has first
End and the second end, first end are connected with proportion electro-magnet, and the second end is threadedly coupled with valve element；
Valve element, the valve element divide top, middle part and bottom, to compensate hydraulic power of the valve element by liquid stream, described
Valve element bottom processes a loop configuration, flow direction change, balances hydraulic power；Valve element upper end thread mill drilling, is used for
It is connected with the valve rod.
Wherein, the valve element upper diameter is more than oil discharge passage；
Wherein, in the middle part of the valve element and bottom it is at least part of can be contained in oil discharge passage and drainback passage and
It can be moved along the direction of the longitudinal axis of two passages.
The valve element each several part diameter is identical with size at valve body cooperation, and proportion electro-magnet push rod, valve rod, valve element with
Exit passageway is coaxial, when valve element and exit passageway and oil return opening channel contact, is formed and coordinated.Valve element coupling part and valve rod
First end connection is removably secured by screw thread or combined, and in valve element upper end by nut check,
The present invention is directed to the problem of electro-hydraulic proportional reducing valve proportion electro-magnet thrust is big, it is proposed that a kind of new differential type
Electric-hydraulic proportion uniform-pressure-drop valve, the pressure-reducing valve can effectively reduce proportion electro-magnet thrust, and implementation is：
Electro-hydraulic proportional reducing valve essence be by liquid stream flow through gap produce the pressure loss, realize decompression, control valve element with
Valve body restriction size can realize decompression, and electric-hydraulic proportion uniform-pressure-drop valve of the invention is by by import oil pressure and outlet oil pressure
The difference of hydrodynamic force and proportion electro-magnet thrust-balancing in the differential area of valve element are acted on, carrys out control orifice size, takes
For conventional electro-hydraulic proportional pressure-reducing valve directly by pressure and the mode of proportion electro-magnet balance, proportion electro-magnet is effectively reduced
Thrust.
When the proportion electro-magnet electrical current is zero, the valve core opening is maximum, and electric-hydraulic proportion of the invention is fixed poor
Pressure-reducing valve does not depressurize, if inlet pressure P1, outlet pressure P2, now P1=P2。
When the proportion electro-magnet input current is not zero, thrust caused by the proportion electro-magnet and the valve element by
Hydraulic coupling compare, be finally reached equilbrium position, the valve element upper diameter is D, the stem diameter and the valve element bottom
Diameter is d1, the valve element mid diameter is d, and now the valve element stress equation is：
Outlet pressure P2The valve element upper end is led to, the valve element upper end is institute by the region of the active force of outlet pressure
The differential area of valve element upper end and the valve rod is stated, the direction of active force is downward along the valve element, and size is：
The valve element lower end is by two different hydraulic couplings:
Wherein, the valve element top is in the middle part of the valve element and on the valve element by the region of the active force of inlet pressure
The differential area in portion, the direction of active force is upward along the valve element, and size is：
Wherein, it is in the middle part of the valve element and valve element bottom by the region of the active force of outlet pressure in the middle part of the valve element
Differential area, the direction of active force is upward along the valve element, and size is：
The thrust of the proportion electro-magnet is FM, wherein FM=ki, ignore the valve element weight and the hydraulic power being subject to, stable state
During balance, the valve element equilibrium equation is：
By adjusting proportion electro-magnet electric current, the oil inlet and outlet pressure of electric-hydraulic proportion uniform-pressure-drop valve of the present invention can be adjusted
Difference.
Brief description of the drawings
Fig. 1 is the internal structure sectional view of the electric-hydraulic proportion uniform-pressure-drop valve of the embodiment of the present invention
Fig. 2 is using the bivariate fax hydrostatic actuating system after a kind of new electric-hydraulic proportion uniform-pressure-drop valve of the present invention
Systematic schematic diagram
Fig. 3 is the valve element schematic diagram of the differential type electric-hydraulic proportion uniform-pressure-drop valve of the present invention
Embodiment
A kind of new electric-hydraulic proportion uniform-pressure-drop valve proposed by the present invention can be used for bivariate fax hydrostatic actuating system
Variable pump discharge capacity regulation in, its add electric-hydraulic proportion uniform-pressure-drop valve after fax hydrostatic actuating system schematic diagram such as
Shown in Fig. 2.
When the hydrostatic of bivariate fax shown in Fig. 2 actuating system works, the rotation of motor 8 drives the output flow of variable pump 9, variable
The flow part that pump 9 exports flows to double acting cylinder 17, and driving double acting cylinder 17 moves along a straight line, so as to drive rudder face 18 to transport
It is dynamic；Another part is entered in single-acting cylinder 10 by shuttle valve 12 by electric-hydraulic proportion uniform-pressure-drop valve 11, and single-acting cylinder 10 is done directly
Line motion driving variable pump 9 swash plate rotation, now the discharge capacity of variable pump 9 diminishes.When the actuating system high pressure chest of fax hydrostatic shown in Fig. 2
During hypertonia, the safety of system can be ensured by the off-load of safety valve 16.By-passing valve 15 is damped in the start of fax hydrostatic shown in Fig. 2
System is opened when breaking down, and the output flow of variable pump 9 directly all returns to the oil return of variable pump 9 through damping by-passing valve 15
Mouthful so that double acting cylinder 8 does not produce driving effect to load, so as to play a part of isolated fault.
When the actuating system of fax hydrostatic shown in Fig. 2 works, by analysis system working condition, understand the power consumption of motor 8 with
The relation of the rotating speed of motor 8, it is assumed that outer load force FLWhen constant, the system output power for loading needs is exactly certain.Thus may be used
Determine the power output P of double acting cylinder 17c(it is defined as the product of outer load force and pressurized strut piston speed, i.e. Pc=FLV), become
Measure the power output P of pump 9p(it is defined as outer load force and the product of flow system flow, i.e. Pp=pLQL), and the output work of motor 8
Rate Pm(it is defined as output torque and the product of rotating speed, i.e. Pm=Temωm).If keeping the power output P of motor 1mConstant feelings
Under condition, output torque can be reduced while 8 rotating speed of motor is increased, it is possible to realize the purpose for reducing the electric current of motor 8.Due to electricity
Machine 8 is connected by a common rotating shaft with variable pump 9 and with identical rotational speed, therefore the output torque T of motoremAnd pump
Load torque TLIt is equal.The load torque T of variable pump 9LEqual to system load pressure and the product of the discharge capacity of variable pump 9, that is, there is TL
=DppL.So when the timing of load one, the discharge capacity can for reducing variable pump 9 reduces load torque, and fax hydrostatic shown in Fig. 2 is made
Dynamic system, load pressure feedback is increased to the swashplate angle of variable pump 9, the swashplate angle of variable pump 9 with pressure, and swashplate angle becomes
Small, then the load torque of motor 8 reduces.
The electric current of motor 8 is again directly proportional to output torque：
Tem=mp ψfIcosψ
After the model of motor 8 determines, other parameters determine in addition to electric current.For motor 8, power consumption mainly includes copper loss Δ PCu、
Iron loss Δ PFeWith windage loss Δ Pm：
Δ P=Δs PCu+ΔPFe+ΔPm
And the copper loss of motor 8 is the main pyrotoxin of motor or even whole fax hydrostatic actuating system, the copper loss of motor 8 is Δ PCu=
3I2R, the loss of electric machine can be effectively reduced by reducing current of electric.
The swashplate angle of variable pump 9 reduces, and causes the reduction of the actuating system of fax hydrostatic shown in Fig. 2 dynamic property, by the present invention
A kind of new electric-hydraulic proportion uniform-pressure-drop valve proposed is added in feedback channel, can utilize the momentary overload capacity of motor in short-term
Between improve the discharge capacity upper limit of variable pump 9, be effectively improved the dynamic property of system, main implementation process：
The discharge capacity of variable pump 9 is relevant with its swashplate angle, its discharge capacity：
D=kp(xmax-xp)
kpFor the discharge coefficient of variable pump 9, xmaxThe maximum displacement exported for single-acting cylinder 10, single-acting cylinder 10 pass through its carry-out bit
Move the control discharge capacity of variable pump 9, it is assumed that the outer load of single-acting cylinder 10 is elastic force, then output displacement
By controlling the discharge capacity into the pressure control variable pump 9 of single-acting cylinder 10：
When load pressure causes the discharge capacity of variable pump 9 to reduce, the electric current of control electric-hydraulic proportion uniform-pressure-drop valve 11, reduce its outlet
Pressure, the increase of the swashplate angle of variable pump 9, discharge capacity increase, so as to improve the dynamic property of system.And at fax hydrostatic actuating system
When stable state, to reduce the load torque of motor 8, it is zero to make the import and export electric current of electric-hydraulic proportion uniform-pressure-drop valve 11, now, electro-hydraulic
Ratio uniform-pressure-drop valve 11 directly exports the load pressure of fax hydrostatic actuating system, and the swashplate angle of variable pump 9 is with load pressure
Increase and reduce, according to TL=DppL, the reduction of the load torque of variable pump 9, the load torque of motor 8 is equal to the load turn of variable pump 9
Square, the electric current of motor 8 reduce, and cause the heat loss of motor 8 to reduce, and improve the energy efficiency of whole system, reduce fax hydrostatic work
The heating of dynamic system.
Obviously, examples detailed above is only intended to clearly illustrate examples of the invention, and is not the reality to the present invention
Apply the restriction of mode.For those of ordinary skill in the field, can also make on the basis of the above description other
Various forms of changes or variation.There is no necessity and possibility to exhaust all the enbodiments.And these belong to the present invention
The obvious changes or variations amplified out of spirit still in protection scope of the present invention among.
Claims (7)
1. a kind of differential type electric-hydraulic proportion uniform-pressure-drop valve, including：
Valve body, there is fluid import, fluid outlet and fluid oil return opening, the valve body import, outlet, oil return opening process spiral shell respectively
Pit, the unthreaded hole that valve body upper end processing coordinates with proportion electro-magnet convex shoulder, ensure sealing with O-ring during cooperation, it is described
Valve body lower end machining internal thread is sealed with hexagonal socket head plug, and after side passageway machining, Outboard Sections are blocked with hydraulic pressure plug.
2. differential type electric-hydraulic proportion uniform-pressure-drop valve according to claim 1, in addition to：
Valve element, the valve element divide top, middle part and bottom, valve element upper end thread mill drilling；
Wherein, the valve element upper diameter is more than oil discharge passage diameter, and the valve element mid diameter is equal to oil discharge passage diameter, institute
State valve element lower diameter and be less than mid diameter；
Wherein, in the middle part of the valve element and bottom is at least part of can be contained in oil discharge passage and drainback passage and can be with
Moved along the direction of the longitudinal axis of two passages.
3. differential type electric-hydraulic proportion uniform-pressure-drop valve according to claim 1, in addition to：
Valve pocket, intake channel, the valve pocket, exit passageway or oil return opening passage form fluid passage, and side passage will export
Pressure guides to the valve element upper end.
4. differential type electric-hydraulic proportion uniform-pressure-drop valve according to claim 1, in addition to：
Proportion electro-magnet, the electric signal converting to force signal that will be obtained, external output action power, the proportion electro-magnet lower end are convex
Shoulder is used to position.
5. differential type electric-hydraulic proportion uniform-pressure-drop valve according to claim 1, in addition to：
Valve rod, the valve rod extend in the valve body and moved along the longitudinal axis of the valve rod；The valve rod has
First end and the second end, first end are connected with the proportion electro-magnet, and the second end is threadedly coupled with valve element；
Valve element each several part diameter proportion electro-magnet push rod identical and described with size at the valve body cooperation, valve rod,
Valve element is coaxial with exit passageway, when the valve element and exit passageway and oil return opening channel contact, is formed and coordinated, the valve element
Coupling part is removably secured by screw thread with the first end of the valve rod and is connected or combines, and is passed through in the valve element upper end
Nut check.
A kind of 6. differential type electric-hydraulic proportion uniform-pressure-drop valve according to claim 1, it is characterised in that：It is proposed by the present invention
A kind of differential type electric-hydraulic proportion uniform-pressure-drop valve, by the differential area that import oil pressure and outlet oil pressure are acted on to the valve element
The difference of upper hydrodynamic force and the proportion electro-magnet thrust-balancing, to control restriction between the valve element and the valve body big
It is small, reach the purpose of control outlet pressure.
A kind of 7. differential type electric-hydraulic proportion uniform-pressure-drop valve according to claim 1, it is characterised in that：The present invention is directed to liquid
When stream flows through valve element, caused liquid stream is to the reaction force of valve element, i.e., the steady-state fluid force that valve element is subject to, and designs a kind of compensation knot
Structure, compensating spool are processed a tapering annular knot by the hydraulic power of liquid stream at the valve element bottom and the valve outlet
Structure, flow direction change, allow at valve outlet at liquid flow path direction and valve body import liquid flow path direction on the contrary, the structure balances institute
State steady-state fluid force of the valve element by liquid stream.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710649136.9A CN107461516A (en) | 2017-08-02 | 2017-08-02 | A kind of differential type electric-hydraulic proportion uniform-pressure-drop valve |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710649136.9A CN107461516A (en) | 2017-08-02 | 2017-08-02 | A kind of differential type electric-hydraulic proportion uniform-pressure-drop valve |
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|---|---|
| CN107461516A true CN107461516A (en) | 2017-12-12 |
Family
ID=60547337
Family Applications (1)
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|---|---|---|---|
| CN201710649136.9A Pending CN107461516A (en) | 2017-08-02 | 2017-08-02 | A kind of differential type electric-hydraulic proportion uniform-pressure-drop valve |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108194433A (en) * | 2017-12-20 | 2018-06-22 | 北京交通大学 | Electromechanical static pressure actuating system |
| CN108488455A (en) * | 2018-04-11 | 2018-09-04 | 王爱菊 | Valve gear and hydraulic system |
| CN108506261A (en) * | 2018-04-11 | 2018-09-07 | 王爱菊 | Pressure regulating method based on valve gear |
| CN108561358A (en) * | 2018-01-22 | 2018-09-21 | 邵立坤 | A kind of differential circuit switching valve and hydraulic differential circuit |
| CN114593101A (en) * | 2022-03-25 | 2022-06-07 | 哈尔滨工业大学 | Multi-stage main pressure logic control valve for compensating steady-state hydraulic power |
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|---|---|---|---|---|
| US5309944A (en) * | 1992-05-19 | 1994-05-10 | Kayaba Kogyo Kabushiki Kaisha | Electromagnetic proportional pressure reducing valve |
| CN101124525A (en) * | 2005-02-11 | 2008-02-13 | Hydac流体技术有限公司 | Valve, especially proportional pressure control valve |
| CN201078364Y (en) * | 2007-08-15 | 2008-06-25 | 新疆石油管理局钻井工艺研究院 | Electromagnetic valve |
| CN201322067Y (en) * | 2008-08-08 | 2009-10-07 | 宁波市鄞州通力液压电器厂 | High-speed switch valve |
| CN106838362A (en) * | 2017-02-09 | 2017-06-13 | 浙江大学 | It is a kind of to fall structure for inserting the balance of valve core hydraulic power elimination |
-
2017
- 2017-08-02 CN CN201710649136.9A patent/CN107461516A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5309944A (en) * | 1992-05-19 | 1994-05-10 | Kayaba Kogyo Kabushiki Kaisha | Electromagnetic proportional pressure reducing valve |
| CN101124525A (en) * | 2005-02-11 | 2008-02-13 | Hydac流体技术有限公司 | Valve, especially proportional pressure control valve |
| CN201078364Y (en) * | 2007-08-15 | 2008-06-25 | 新疆石油管理局钻井工艺研究院 | Electromagnetic valve |
| CN201322067Y (en) * | 2008-08-08 | 2009-10-07 | 宁波市鄞州通力液压电器厂 | High-speed switch valve |
| CN106838362A (en) * | 2017-02-09 | 2017-06-13 | 浙江大学 | It is a kind of to fall structure for inserting the balance of valve core hydraulic power elimination |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108194433A (en) * | 2017-12-20 | 2018-06-22 | 北京交通大学 | Electromechanical static pressure actuating system |
| CN108561358A (en) * | 2018-01-22 | 2018-09-21 | 邵立坤 | A kind of differential circuit switching valve and hydraulic differential circuit |
| CN108488455A (en) * | 2018-04-11 | 2018-09-04 | 王爱菊 | Valve gear and hydraulic system |
| CN108506261A (en) * | 2018-04-11 | 2018-09-07 | 王爱菊 | Pressure regulating method based on valve gear |
| CN114593101A (en) * | 2022-03-25 | 2022-06-07 | 哈尔滨工业大学 | Multi-stage main pressure logic control valve for compensating steady-state hydraulic power |
| CN114593101B (en) * | 2022-03-25 | 2022-09-02 | 哈尔滨工业大学 | Multi-stage main pressure logic control valve for compensating steady-state hydraulic power |
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Application publication date: 20171212 |