CN107725840A - The proportional flow stop valve of double-direction control - Google Patents
The proportional flow stop valve of double-direction control Download PDFInfo
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- CN107725840A CN107725840A CN201711088663.3A CN201711088663A CN107725840A CN 107725840 A CN107725840 A CN 107725840A CN 201711088663 A CN201711088663 A CN 201711088663A CN 107725840 A CN107725840 A CN 107725840A
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- Prior art keywords
- valve
- damping hole
- hydraulic fluid
- fluid port
- pilot
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Classifications
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- 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
- F16K15/00—Check valves
- F16K15/02—Check valves with guided rigid valve members
- F16K15/06—Check valves with guided rigid valve members with guided stems
- F16K15/063—Check valves with guided rigid valve members with guided stems the valve being loaded by a spring
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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
- F15B13/027—Check valves
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- 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
- F16K15/00—Check valves
- F16K15/18—Check valves with actuating mechanism; Combined check valves and actuated valves
- F16K15/182—Check valves with actuating mechanism; Combined check valves and actuated valves with actuating mechanism
- F16K15/1826—Check valves which can be actuated by a pilot valve
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- 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
- F16K31/0644—One-way valve
- F16K31/0655—Lift valves
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- 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
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
- F16K31/40—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor
- F16K31/406—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor acting on a piston
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
The present invention proposes a kind of proportional flow stop valve of double-direction control, it is characterised in that including：Proportion electro-magnet, the swivel nut that one end is connected with the proportion electro-magnet, the armature being actively installed in the swivel nut, one end are fixedly connected on the valve pocket of the other end of the swivel nut, and the other end of the valve pocket is provided with hydraulic fluid port A and hydraulic fluid port B；The main valve plug being connected in the valve pocket, the first damping hole connected with hydraulic fluid port B and the second damping hole connected with hydraulic fluid port A are which is provided with, and the diameter of the first damping hole is more than the diameter of the second damping hole；The guide's valve pocket being actively socketed in the main valve plug, which is provided with pilot chamber and the 3rd damping hole；And pilot valve, its one end is fixedly connected on the other end of the armature, the other end of pilot valve passes through control chamber, pilot chamber and the second damping hole, and the other end of pilot valve is provided with the conehead section being engaged with the second damping hole, and the conehead section can block the second damping hole.The proportional flow stop valve structure is simple, cost is low and can realize double-direction control.
Description
Technical field
The present invention relates to valve technology field, and in particular to a kind of proportional flow stop valve of double-direction control.
Background technology
In recent years, proportional flow stop valve lifts in truck-mounted crane, high-altitude operation vehicle, tractor rotary tillage plough, electri forklift etc.
Using more and more in equipment.When equipment stops, proportional flow stop valve plays a part of pressurize, prevents hydraulic cylinder from gliding；
When equipment needs to decline, proportional flow stop valve controls openings of sizes, adjusts hydraulic cylinder according to the voltage signal size of input
The flow of output, and then control the decrease speed of jacking equipment.The proportional flow stop valve that currently there are, can only be realized
The control of unidirectional proportional flow, that is to say, that hydraulic oil from the hydraulic fluid port B of proportional flow stop valve flow into hydraulic fluid port A when can be real
If existing proportional flow control, that hydraulic oil when hydraulic fluid port A flows into hydraulic fluid port B only unidirectional valve action, can not be completed proportional flow
Control.As patent publication No. be CN 105298967A, entitled " a kind of big-powered tractor lifter valve group " patent of invention
In provide for it is a kind of control tractor lifting mechanism hydraulic valve bank, wherein just employing 2 proportional flow stop valves, use respectively
In the raising and lowering speed regulation of control lifter.It is expensive due to proportioning valve, using 2 proportional flow stop valve gesture
The rising of cost must be caused, limits extensive use of the proportional flow stop valve on the relatively low main frame of some prices.
The content of the invention
For some or all of of the above-mentioned technical problem in the presence of prior art, the present invention proposes a kind of two-way
The proportional flow stop valve of control, the proportional flow stop valve structure is simple, cost is low and can realize double-direction control.
In order to realize above goal of the invention, the present invention proposes a kind of proportional flow of the double-direction control with following structure
Stop valve, including：
Proportion electro-magnet,
Swivel nut, its one end are connected with the proportion electro-magnet；
Armature, it is actively installed in the swivel nut, and its one end is connected in the proportion electro-magnet by elastic component；
Valve pocket, its one end are fixedly connected on the other end of the swivel nut, and the other end of the valve pocket is provided with hydraulic fluid port A and oil
Mouth B；
Main valve plug, it is connected in the valve pocket, be which is provided with the first damping hole connected with hydraulic fluid port B and is connected with hydraulic fluid port A
The second logical damping hole, the diameter of first damping hole are more than the diameter of the second damping hole；
Guide's valve pocket, it is actively socketed in the main cavity of the main valve plug, and hydraulic fluid port is provided with close to hydraulic fluid port A one end
The pilot chamber of A openings and the 3rd damping hole connected with pilot chamber, the 3rd damping hole can be with the described first dampings
Hole connects；And
Pilot valve, its one end are fixedly connected on the other end of the armature, the other end of pilot valve through control chamber,
Pilot chamber and the second damping hole, and the other end of the pilot valve is provided with the conehead section being engaged with the second damping hole, institute
The second damping hole can be blocked by stating conehead section；
When pilot valve movement drives pilot valve set mobile, by controlling the voltage swing of proportion electro-magnet to control the
One damping hole, the unlatching of the second damping hole and main valve plug, closing and openings of sizes are so as to forming to hydraulic fluid port A or hydraulic fluid port B oil-feeds
When bidirectional throttle control.
In the present invention, it is respectively controlled unlike being provided with multiple ratio one-way flow valves in the prior art, but it is logical
Cross the internal structure of design proportion flow stop valve so that by controlling the voltage swing of proportion electro-magnet with regard to the first resistance can be controlled
Buddhist nun hole, the unlatching of the second damping hole and main valve plug, closing and openings of sizes, realize by a proportional flow stop valve with regard to energy
Bidirectional throttle control during to hydraulic fluid port A or hydraulic fluid port B oil-feeds is realized, thus structure is simpler, cost is lower.
In one embodiment, the control chamber is by armature lower surface, the middle part of swivel nut, the top of valve pocket, main valve
Chamber that upper end, guide's valve pocket and the pilot valve of core are formed, positioned at main valve plug upper end, the control chamber and the guide
Chamber.A relatively large control chamber of volume is formd, it is convenient to carry out multistage ratio control.
In one embodiment, guide's valve pocket follow the pilot valve towards proportion electro-magnet move when, institute
State the first damping hole and be moved to pent position again to throttle position from the throttle position turned on the 3rd damping hole.First resistance
When Buddhist nun hole is staggered with the 3rd damping hole, guide's valve pocket blocks the first damping hole, and the fluid of the first damping hole can not enter first guide cavity,
First damping hole is in the closed position.
In one embodiment, the pilot valve follow the armature towards proportion electro-magnet move when, described
Two damping holes are moved to throttle from the closed position blocked by pilot valve.
In one embodiment, the middle part of the pilot valve is provided with the annular groove for connecting, the pilot valve
Set is fixedly connected through connector, the annular groove with the pilot valve.Connector connects guide's valve pocket and pilot valve, because
And when pilot valve follows armature to move up, guide's valve pocket also follows pilot valve synchronously to move up.
In one embodiment, one end that the pilot valve connects the armature is T-type structure, the one of the armature
End is provided with the first T-shaped hole coordinated with the T-type structure of the pilot valve, and the other end of the armature is provided with the second T-shaped hole, institute
The one end for stating elastic component is arranged in the macropore in the described second T-shaped hole, and the first T-shaped hole connects with the second T-shaped hole.First T
Type hole and the structure in the second T-shaped hole, had both ensured the function-stable of elastic component, and and can ensures that pilot valve is synchronous with armature motion
Property.
In one embodiment, during hydraulic fluid port B oil-feeds, give proportion electro-magnet one voltage, the armature overcomes described
The active force of elastic component, the pilot valve is driven to move upwards, the first damping hole is blocked in motion to guide's valve pocket upwards, the
Two damping holes are opened, and the pressure of control chamber declines, and the differential pressure action of hydraulic fluid port B and control chamber is on main valve plug；
The pressure difference increase of voltage on scaling up electromagnet, hydraulic fluid port B and control chamber, main valve plug are opened, hydraulic fluid port B fluid
Hydraulic fluid port A is moved to through main valve plug；
Voltage on further scaling up electromagnet, the area of passage between pilot valve and the second damping hole reach most
Greatly, the first damping hole completely closes, and main valve plug fully opens.
During hydraulic fluid port B oil-feeds, realize that the throttling from hydraulic fluid port B to hydraulic fluid port A fluid controls.
In one embodiment, during hydraulic fluid port A oil-feeds, first give proportion electro-magnet one voltage so that at guide's valve pocket
In the position for blocking the first damping hole completely, the second damping hole fully opens；
The voltage of scaling up electromagnet, the first damping hole are progressively opened, and the area of passage of the first damping hole is progressively big
In the area of passage of the second damping hole, main valve plug is gradually opened under hydraulic fluid port A and the differential pressure action of control chamber；
The voltage of further scaling up electromagnet, main valve plug reach maximum opening.
It is understood that during hydraulic fluid port A oil-feeds, if proportion electro-magnet voltage is not given, equivalent to common check valve.For
Realize and controlled from hydraulic fluid port A to hydraulic fluid port B ratio, then start to need first to give one sufficient voltage of proportion electro-magnet and cause elder generation
Guide valve bushing is in the position for blocking the first damping hole completely, then again from hydraulic fluid port A oil-feeds.
In a preferred embodiment, the valve pocket is connected with the other end thread seal of the swivel nut, the master
The lower end of valve element and the junction of the valve pocket are provided with inclined-plane.In order to realize that better seal connects, the structure on inclined-plane is in main valve
Pressurize can be achieved before opening in core.
Compared with prior art, the present invention has advantages below：
1) present invention can be realized double from hydraulic fluid port A to hydraulic fluid port B and from hydraulic fluid port B to hydraulic fluid port A by a proportional directional valve
To control；It is middle compared with the prior art to use multiple proportioning valves, cost is not only greatly reduced, and reduce the multiple valves of installation
Difficulty, area occupied are small；
2) for the present invention compares existing bidirectional control valve, parts are less, structure is simpler, using more reliable；Also drop
Low manufacturing process difficulty and manufacturing cost.
Brief description of the drawings
The preferred embodiments of the present invention are described in detail below in conjunction with accompanying drawing, in figure：
Fig. 1 show the structural representation of one of embodiment of the proportional flow stop valve of the double-direction control of the present invention
Figure；
Fig. 2 show one of position view of the embodiment in hydraulic fluid port B oil-feeds in Fig. 1；
Fig. 3 show Fig. 2 the latter position view；
Fig. 4 show one of position view of the embodiment in hydraulic fluid port A oil-feeds in Fig. 1；
Fig. 5 show Fig. 4 the latter position view；
Fig. 6 show the principle schematic of the hydraulic system of the proportional flow stop valve of the double-direction control using the present invention.
In accompanying drawing, identical part uses identical reference.Accompanying drawing is not drawn according to the ratio of reality.
Embodiment
In order that technical scheme and advantage are more clearly understood, below in conjunction with accompanying drawing to the exemplary of the present invention
Embodiment is described in more detail.Obviously, described embodiment is only the part of the embodiment of the present invention, rather than
The exhaustion of all embodiments.And in the case where not conflicting, the feature in embodiment and embodiment in the present invention can be mutual
It is combined.
Inventor is during invention it is noted that existing proportional flow stop valve can only realize unidirectional proportional flow
Control, limit the application of proportional flow stop valve.
Deficiency, embodiments of the invention propose a kind of proportional flow stop valve of double-direction control, entered below for more than
Row explanation.
Fig. 1 shows the one of which embodiment of the proportional flow stop valve of the double-direction control of the present invention.In the embodiment
In, the proportional flow stop valve of double-direction control of the invention mainly includes：Proportion electro-magnet 1, swivel nut 2, armature 7, main valve plug 4,
Guide's valve pocket 5 and pilot valve 6.Wherein, one end of swivel nut 2 is fixedly connected with proportion electro-magnet 1, and the other end of swivel nut 2 passes through
Valve pocket 3 is threadedly coupled, the one end of valve pocket 3 away from swivel nut 2 is provided with hydraulic fluid port A and hydraulic fluid port B.Main valve plug 4 is connected in valve pocket 3, its
It is provided with the first damping hole 8 connected with hydraulic fluid port B and the second damping hole 9 connected with hydraulic fluid port A, the diameter of the first damping hole 8 is big
In the diameter of the second damping hole 9.Guide's valve pocket 5 is actively socketed in the main chamber of main valve plug 6, and guide is provided with guide's valve pocket 5
Chamber and the 3rd damping hole 12 connected with pilot chamber.One end of pilot valve 6 is fixedly connected on armature 7, pilot valve
The other end of core 6 passes through control chamber 10, pilot chamber and the second damping hole 9.
In one embodiment, shape is provided with conehead section 61 at corresponding second damping hole 9 of pilot valve 6, it will therefore be appreciated that
, as shown in figure 1, pilot valve 6, when not rising, its conehead section 61 is leaned against on the second damping hole 9, now the second damping hole
9 are closed.
In one embodiment of the invention, pilot valve 6 follow armature 7 towards proportion electro-magnet 1 move when, second resistance
Buddhist nun hole 9 is moved to throttle from the closed position blocked by the conehead section 61 of the lower end of pilot valve 6.
In one embodiment, as shown in Figures 1 to 5, control chamber 10 is by the lower surface of armature 7, the middle part of swivel nut 2, valve
It is that the top of set 3, the upper end of main valve plug 4, the upper end of guide's valve pocket 5 and pilot valve 6 are formed, positioned at the upper end of main valve plug 4
Chamber.Control chamber 10 connects with pilot chamber.Herein, a relatively large control chamber of volume 10 is formd to facilitate progress more
Level ratio control.It is understood that the control chamber 10 shown in embodiment is one kind therein, actually can be in several ways
To change the volume size and shape of control chamber, such as the shape of change valve pocket 3 upper end to change the shapes and sizes of control chamber
Deng.
In one embodiment, guide's valve pocket 5 follow pilot valve 6 towards the direction of proportion electro-magnet 1 (Fig. 3 show to
On) it is mobile when, the first damping hole 8 is moved to both from throttle position turn on the 3rd damping hole 12 and is not turned on, and first damps
The closed position that hole 8 is blocked by guide's valve pocket 5.Herein, when the first damping hole 8 and the 3rd damping hole 12 stagger, guide's valve pocket 5 hides
The first damping hole 8 is kept off, the fluid of the first damping hole 8 can not enter first guide cavity, and the first damping hole 8 is in the closed position, pilot valve
Set 5 continues to move up, then the first damping hole 8 is slowly opened again.
In a preferred embodiment, the middle part of pilot valve 6 is provided with the annular groove 61 for connecting, guide's valve pocket
5 are fixedly connected through connector, annular groove 61 with pilot valve 6.It is, guide's valve pocket 5 and guide are connected by connector
Valve element 6, when pilot valve 6 follows armature 7 to move up, guide's valve pocket 5 also follows pilot valve 6 synchronously to move up.
In a preferred embodiment, one end that pilot valve 6 connects armature 7 is T-type structure, and one end of armature 7 (is schemed
It is upper end in 1) it is provided with the first T-shaped hole coordinated with the T-type structure of pilot valve 6, the other end (being lower end in Fig. 1) of armature 7
Provided with the second T-shaped hole, one end of elastic component 11 is arranged in the macropore in the second T-shaped hole, and the first T-shaped hole connects with the second T-shaped hole.
In one embodiment, during hydraulic fluid port B oil-feeds, give proportion electro-magnet 1 one voltages, armature 7 overcomes elastic component 11
Active force, drive pilot valve 6 move upwards, guide's valve pocket 5 upwards motion block the first damping hole 8, the second damping hole 9 is opened
Open, the pressure of control chamber 10 declines, and the differential pressure action of hydraulic fluid port B and control chamber 10 is on main valve plug 4.On scaling up electromagnet 1
Voltage, the pressure difference of hydraulic fluid port B and control chamber 10 increases, and main valve plug 4 is opened, and hydraulic fluid port B fluid is moved to hydraulic fluid port A through main valve plug 4.
Voltage on further scaling up electromagnet 1, the area of passage between the damping hole 9 of pilot valve 6 and second reaches maximum, main
Valve element 4 fully opens.
In one embodiment, during hydraulic fluid port A oil-feeds, first give proportion electro-magnet 1 one voltages so that at guide's valve pocket 5
In the position (as shown in Figure 4) for blocking the first damping hole 8 completely.The voltage of scaling up electromagnet 1, the first damping hole 8 is progressively
Open, when the excessively stream flow area of the first damping hole is more than the area of passage of the second damping hole, main valve plug 4 is in hydraulic fluid port A and control
Gradually opened under the differential pressure action of chamber 10.The voltage of further scaling up electromagnet 1, main valve plug 4 reach maximum opening.
In an embodiment of the present invention, when the drive guide of pilot valve 6 valve pocket 5 moves up, by controlling ratio electromagnetism
The voltage swing of iron 1 can control unlatching, closing and the openings of sizes of the first damping hole 8, the second damping hole 9 and main valve plug 4, from
And form bidirectional throttle control during to hydraulic fluid port A or hydraulic fluid port B oil-feeds.The specific course of work is introduced in detail below.
If hydraulic fluid port B oil-feeds, when proportion electro-magnet 1 is given certain voltage, proportion electro-magnet 1 produces certain suction
Power, armature 7 overcome the effect of spring 11 to produce certain displacement in the presence of the suction, drive pilot valve 6 to be separated from the
Two damping holes 9, guide's valve pocket 5, which moves up, slowly covers in the first damping hole 8 (as shown in Figure 2).The now pressure of control chamber 10
Power will decline, and the pressure initiation pressure difference in hydraulic fluid port B pressure and control chamber 10, this differential pressure action is on main valve plug 4 (due to main valve
Core 4 and stairstepping, produce difference in areas), but now make a concerted effort also to be not enough to promote main valve plug 4 to rise.
Continue to increase the voltage on proportion electro-magnet 10, the first damping hole 8 is further covered, and the second damping hole 9 enters one
Step is opened, and the pressure difference increase in hydraulic fluid port B pressure and control chamber 10, main valve plug 4 is begun to move up, and hydraulic fluid port B fluid flows to
Hydraulic fluid port A (as shown in Figure 3).
Continuing to increase the voltage of given proportion electro-magnet 1, guide's valve pocket 5 will be completely covered by the first damping hole 8,
Area of passage between second damping hole 9 and pilot valve 6 reaches maximum, and now main valve plug 4 fully opens.
If hydraulic fluid port A oil-feeds, it is necessary to first give the enough initial voltage of proportion electro-magnet 1, make guide's valve pocket 5 be in quilt completely
The initial control position (as shown in Figure 4) covered in, now the second damping hole reach maximum slotted density.In the base of initial voltage
On plinth, voltage signal is gradually increased, by the cone structure of the bottom of guide's valve pocket 5, the first damping hole 8 is progressively opened, and guide
During valve element 6 gradually rises, the area of passage of the second damping hole will not produce change.Namely the first damping hole 8
Area slowly becomes big, and the increasingly greater than area of passage of the second damping hole, and the pressure of such control chamber 10 and the pressure of B mouths are more next
Closer, the pressure difference between the pressure and A mouth pressure of control chamber 10 is increasing, as shown in figure 5, so main valve plug 4 is being made a concerted effort
In the presence of, progressively open, hydraulic fluid port A to hydraulic fluid port B flow become larger.
In accordance with the above, the maximum voltage of proportion electro-magnet 1 is given during hydraulic fluid port A oil-feeds, main valve plug 4 can reach maximum and hold
Degree, now hydraulic fluid port A to hydraulic fluid port B flowings are up to maximum stream flow.If not giving the voltage of proportion electro-magnet 1, pilot valve 6 is in and sealed
The position (as shown in Figure 1) of second damping hole 9, hydraulic fluid port A to hydraulic fluid port B are flowed equivalent to check valve, can also reach maximum stream flow.Cause
This, maximum stream flow control can give the maximum voltage of proportion electro-magnet 1 and not the check valve work(to voltage by hydraulic fluid port A oil-feeds
Can both modes realize.
In order to better illustrate the effect of the proportional flow stop valve of the double-direction control of the present invention, as Fig. 6 shows one
Using the principle schematic of the hydraulic system of the proportional flow stop valve 15 of the double-direction control of the present invention.In the figure, hydraulic pump
13 fluid out pass through the solenoid directional control valve 14 of two-bit triplet, if the left side of solenoid directional control valve 14 of two-bit triplet must be electric, change
Back into the proportional flow stop valve 15 of the double-direction control of the present invention, giving proportion electro-magnet 1 sufficient initial voltage feelings
Under condition, fluid controllably flows to hydraulic fluid port B through hydraulic fluid port A, then enters hydraulic cylinder 16 by the road.
If the solenoid directional control valve 14 of two-bit triplet as shown in Figure 6 must not electricity be operated in right positions, then hydraulic cylinder
16 fluid is through hydraulic fluid port B, and in the case where giving 1 corresponding voltage of proportion electro-magnet, fluid is in a manner of ratio controls from oil
Mouth B flows to hydraulic fluid port A, then returns to fuel tank through solenoid directional control valve 14.In the case of this kind, if desired midway stops declining, then to ratio
Electromagnet 1 powers off, and the proportional flow stop valve 15 of double-direction control of the invention can play a part of pressurize.
In the present invention, it is respectively controlled unlike being provided with multiple proportional directional valves in the prior art, but by setting
Count the internal structure of proportional directional valve so that by control the voltage swing of proportion electro-magnet 1 with regard to can control the first damping hole 8,
Unlatching, closing and the openings of sizes of second damping hole 9 and main valve plug 4, realize and can be achieved with pair by a proportional directional valve
Hydraulic fluid port A or bidirectional throttle control during hydraulic fluid port B oil-feeds, thus structure is simpler, cost is lower.
In addition, explanation, core technology of the invention are：The damping hole 8 of guide's valve pocket 5 and first composition first is variable
Throttling, the damping hole 9 of pilot valve 6 and second form the second variable restrictor, hydraulic oil from hydraulic fluid port B flow into hydraulic fluid port A when, control first
The area of variable restrictor is less than the area of the second variable restrictor, and main valve plug 4 will be opened slowly, and the area of the first variable restrictor is got over
Small, the area of the second variable restrictor is bigger, and main valve plug 4 is opened bigger.Hydraulic oil from hydraulic fluid port A flow into hydraulic fluid port B when, first allow second
Variable restrictor reaches maximum slotted density, and the first area of passage is minimum, then incrementally increases the area of the first variable restrictor, when the
When the area of passage of one variable restrictor is more than the second damping hole area of passage, main valve plug 4 will be opened slowly, the first variable restrictor
Area continue to increase, the unlatching of main valve plug 4 is bigger.
Although preferred embodiments of the present invention have been described, but those skilled in the art once know basic creation
Property concept, then can make other change and modification to these embodiments.Therefore, appended claims are intended to be construed to include excellent
Select embodiment and fall into having altered and/or changing for the scope of the invention, the change made according to an embodiment of the invention and/
Or modification should be all included within the scope of the present invention.
Claims (9)
- A kind of 1. proportional flow stop valve of double-direction control, it is characterised in that including：Proportion electro-magnet,Swivel nut, its one end are connected with the proportion electro-magnet；Armature, it is actively installed in the swivel nut, and its one end is connected in the proportion electro-magnet by elastic component；Valve pocket, its one end are fixedly connected on the other end of the swivel nut, and the other end of the valve pocket is provided with hydraulic fluid port A and hydraulic fluid port B；Main valve plug, it is connected in the valve pocket, be which is provided with the first damping hole connected with hydraulic fluid port B and is connected with hydraulic fluid port A Second damping hole, the diameter of first damping hole are more than the diameter of the second damping hole；Guide's valve pocket, it is actively socketed in the main valve plug, and the guide of hydraulic fluid port A openings is provided with close to hydraulic fluid port A one end Chamber and the 3rd damping hole connected with pilot chamber, the 3rd damping hole can connect with first damping hole；AndPilot valve, its one end are fixedly connected on the other end of the armature, and the other end of pilot valve passes through control chamber and elder generation Guide cavity room, and the other end of the pilot valve is provided with the conehead section being engaged with the second damping hole, the conehead section can block Second damping hole；When the pilot valve movement drives pilot valve set mobile, by controlling the voltage swing of proportion electro-magnet to control the first resistance Buddhist nun hole, the unlatching of the second damping hole and main valve plug, closing and openings of sizes are so as to forming during to hydraulic fluid port A or hydraulic fluid port B oil-feeds Bidirectional throttle controls.
- 2. proportional flow stop valve according to claim 1, it is characterised in that the control chamber be by armature lower surface, It is that the middle part of swivel nut, the top of valve pocket, the upper end of main valve plug, guide's valve pocket and pilot valve are formed, positioned at main valve plug upper end Chamber, the control chamber connects with the pilot chamber.
- 3. proportional flow stop valve according to any one of claim 1 to 2, it is characterised in that guide's valve pocket with With the pilot valve towards proportion electro-magnet move when, first damping hole is from the throttle position turned on the 3rd damping hole It is moved to pent position and arrives throttle position again.
- 4. proportional flow stop valve according to any one of claim 1 to 3, it is characterised in thatThe pilot valve follow the armature towards proportion electro-magnet move when, second damping hole seals from by pilot valve Stifled closed position is moved to throttle.
- 5. proportional flow stop valve according to claim 4, it is characterised in that the middle part of the pilot valve, which is provided with, to be used for The annular groove of connection, guide's valve pocket are fixedly connected through connector, the annular groove with the pilot valve.
- 6. proportional flow stop valve according to any one of claim 1 to 5, it is characterised in that the pilot valve connects The one end for connecing the armature is T-type structure, and one end of the armature is provided with coordinate with the T-type structure of the pilot valve first T-shaped hole, the other end of the armature are provided with the second T-shaped hole, and one end of the elastic component is arranged on the macropore in the described second T-shaped hole In, the first T-shaped hole connects with the second T-shaped hole.
- 7. proportional flow stop valve according to any one of claim 1 to 6, it is characterised in that during hydraulic fluid port B oil-feeds, give One voltage of proportion electro-magnet is given, the armature overcomes the active force of the elastic component, drives the pilot valve to move upwards, The first damping hole is blocked in motion to guide's valve pocket upwards, and the second damping hole is opened, and the pressure of control chamber declines, hydraulic fluid port B and control The differential pressure action of chamber processed is on main valve plug；The pressure difference increase of voltage on scaling up electromagnet, hydraulic fluid port B and control chamber, main valve plug are opened, and hydraulic fluid port B fluid is through master Valve element is moved to hydraulic fluid port A；Voltage on further scaling up electromagnet, the area of passage between pilot valve and the second damping hole reach maximum, First damping hole completely closes, and main valve plug fully opens.
- 8. proportional flow stop valve according to any one of claim 1 to 7, it is characterised in that during hydraulic fluid port A oil-feeds, give Give one voltage of proportion electro-magnet so that guide's valve pocket is in the position for blocking the first damping hole completely；The voltage of scaling up electromagnet, the first damping hole is progressively opened and the area of passage of the first damping hole is progressively more than second The area of passage of damping hole, main valve plug are gradually opened under hydraulic fluid port A and the differential pressure action of control chamber；The voltage of further scaling up electromagnet, main valve plug reach maximum opening.
- 9. the proportional flow stop valve according to any one of claim 1 to 8, it is characterised in that the valve pocket with it is described The other end thread seal connection of swivel nut, the lower end of the main valve plug and the junction of the valve pocket are provided with inclined-plane.
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| CN201711088663.3A CN107725840B (en) | 2017-11-08 | 2017-11-08 | Bidirectional control proportional flow stop valve |
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| CN201711088663.3A CN107725840B (en) | 2017-11-08 | 2017-11-08 | Bidirectional control proportional flow stop valve |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108916459A (en) * | 2018-07-14 | 2018-11-30 | 东莞海特帕沃液压科技有限公司 | A kind of two-way shut-off valve |
| CN109253304A (en) * | 2018-10-19 | 2019-01-22 | 中国航发贵州红林航空动力控制科技有限公司 | A kind of miniature big flow fuel solenoid valve of 2/2-way normally closed type |
| CN109373021A (en) * | 2018-12-19 | 2019-02-22 | 重庆红江机械有限责任公司 | A kind of fuel oil Automatic Recirculation Valve |
| CN109973456A (en) * | 2019-04-16 | 2019-07-05 | 武汉科技大学 | A kind of automatically controlled high pressure check valve of combined type |
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| CN107725840B (en) | 2020-06-09 |
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