CN107725842A - The ratio one-way flow valves of double-direction control - Google Patents
The ratio one-way flow valves of double-direction control Download PDFInfo
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- CN107725842A CN107725842A CN201711088829.1A CN201711088829A CN107725842A CN 107725842 A CN107725842 A CN 107725842A CN 201711088829 A CN201711088829 A CN 201711088829A CN 107725842 A CN107725842 A CN 107725842A
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- Prior art keywords
- hydraulic fluid
- fluid port
- pilot valve
- damping hole
- valve
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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 ratio one-way flow valves 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 less than the diameter of the second damping hole；And pilot valve, its one end are fixedly connected on the other end of the armature, the other end of pilot valve is slidably arranged in main valve plug, and main valve plug endoporus is divided into control chamber and first guide cavity, and the throttling channel of connection control chamber and first guide cavity is provided with pilot valve.The ratio one-way flow valves of the double-direction control are simple in construction, 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 ratio one-way flow valves of double-direction control.
Background technology
In recent years, the ratio one-way flow valves of double-direction control truck-mounted crane, high-altitude operation vehicle, tractor rotary tillage plough, it is electronic
Using more and more on the jacking equipments such as fork truck.When equipment stops, the ratio one-way flow valves of double-direction control play pressurize
Effect, prevents hydraulic cylinder from gliding；When equipment needs to decline, the ratio one-way flow valves of double-direction control are believed according to the voltage of input
Number size, openings of sizes, the flow of regulation hydraulic cylinder output are controlled, and then control the decrease speed of jacking equipment.Existing market
Present on double-direction control ratio one-way flow valves, the control of unidirectional proportional flow can only be realized, that is to say, that hydraulic oil
If proportional flow control being realized when flowing into hydraulic fluid port A from the hydraulic fluid port B of the ratio one-way flow valves of double-direction control, that hydraulic pressure
Oil from hydraulic fluid port A flow into hydraulic fluid port B when only unidirectional valve action can not be completed proportional flow control.If patent publication No. is CN
105298967 A, entitled " a kind of big-powered tractor lifter valve group " patent of invention in provide for a kind of control and drag
The hydraulic valve bank of machine drawing lifter, wherein just employing the ratio one-way flow valves of 2 double-direction controls, it is respectively used to control lifting
The raising and lowering speed regulation of device.It is expensive due to proportioning valve, using the ratio one-way flow valves gesture of 2 double-direction controls
The rising of cost must be caused, limits the ratio one-way flow valves of double-direction control extensively should on the relatively low main frame of some prices
With.
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 ratio one-way flow valves of control, the ratio one-way flow valves of the double-direction control are simple in construction, cost is low and can realize two-way control
System.
In order to realize above goal of the invention, it is unidirectional that the present invention proposes a kind of ratio of the double-direction control with following structure
Flow 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 the first damping hole are less than the diameter of the second damping hole,；
Pilot valve, its one end are fixedly connected on the other end of the armature, and the other end of pilot valve is slidably arranged in
In the endoporus of main valve plug, cylinder convex shoulder and tiltedly is sequentially provided with corresponding second damping hole of the pilot valve other end from top to bottom
Main valve plug endoporus is separated into the control chamber communicated with the first damping hole and communicated with the second damping hole by face, the cylinder convex shoulder
First guide cavity, the inclined-plane can block the second damping hole, and the throttling channel of connection control chamber and first guide cavity is provided with the cylinder convex shoulder,
The throttling channel is arranged to：When pilot valve moves up, throttling channel opening area is less and less, until closing；
When the armature drives the pilot valve movement, by controlling the voltage swing of proportion electro-magnet to control the secondth
Unlatching, closing and the openings of sizes of damping hole and pilot valve throttling channel are double during to hydraulic fluid port A or hydraulic fluid port B oil-feeds so as to be formed
Controlled to throttling.
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 controlling the voltage swing of proportion electro-magnet with regard to the second damping hole and elder generation can be controlled
Unlatching, closing and the openings of sizes of guide valve core throttling channel, realization can be achieved with to hydraulic fluid port A or oil by a proportional directional valve
Bidirectional throttle control during mouth B oil-feeds, 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 the upper end of core and pilot valve are formed, positioned at main valve plug upper end, the control chamber connect with second damping hole
It is logical.A relatively large control chamber of volume is formd, it is convenient to carry out multistage ratio control.
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 second damping hole is opened, and the pressure of control chamber declines, hydraulic fluid port B
Differential pressure action with 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, 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 pilot valve
In opening the second damping hole completely, pilot valve throttling channel area of passage just starts the position reduced,
Continue the voltage of scaling up electromagnet, the area of passage of pilot valve throttling channel reduces, main valve plug hydraulic fluid port A with
Gradually opened under the differential pressure action of control chamber；
The voltage of further scaling up electromagnet, pilot valve throttling channel are shut completely, and main valve plug reaches 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 core is in the position for opening the second 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 from hydraulic fluid port A to hydraulic fluid port B by the ratio one-way flow valves of a double-direction control and from oil
Mouth B to hydraulic fluid port A double-direction control；It is middle compared with the prior art to use multiple proportioning valves, cost is not only greatly reduced, and reduce
The difficulty of the multiple valves of installation, 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 ratio one-way flow valves 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 structural representation of the hydraulic system of the ratio one-way flow valves 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 the ratio one-way flow valves of existing double-direction control can only realize one direction
Proportional flow control, limit the applications of the ratio one-way flow valves of double-direction control.
Deficiency, embodiments of the invention propose a kind of ratio one-way flow valves of double-direction control, entered below for more than
Row explanation.
Fig. 1 shows the one of which embodiment of the ratio one-way flow valves of the double-direction control of the present invention.In the embodiment
In, the ratio one-way flow valves of double-direction control of the invention mainly include：Proportion electro-magnet 1, swivel nut 2, armature 7, the and of main valve plug 4
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 is connected through a screw thread valve pocket
3, 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, which is provided with and hydraulic fluid port B
First damping hole 8 of connection and the second damping hole 9 connected with hydraulic fluid port A, the diameter of the first damping hole 8 are less than the second damping hole 9
Diameter.One end of first pilot valve 6 is fixedly connected on armature 7, and the other end of pilot valve 6 is slidably arranged in main valve plug 4
Endoporus in, be sequentially provided with cylinder convex shoulder 61 and inclined-plane 63 from top to bottom at corresponding second damping hole 9 of the other end of pilot valve 6,
The endoporus of main valve plug 4 is separated into the control chamber 10 communicated with the first damping hole 8 and communicated with the second damping hole 9 by cylinder convex shoulder 61
First guide cavity, inclined-plane 63 can block the second damping hole 9, and the throttling channel of connection control chamber 10 and first guide cavity is provided with cylinder convex shoulder 61
62, throttling channel 62 is arranged to：When pilot valve 6 moves up, the opening area of throttling channel 62 is less and less, until closing.
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
Chamber that the upper end on the top of set 3, the upper end of main valve plug 4 and pilot valve 6 is formed, positioned at the upper end of main valve plug 4.Control chamber
10 connect with the second damping hole 9.Herein, form a relatively large control chamber of volume 10 and carry out multistage ratio control to facilitate
System.It is understood that the control chamber 10 shown in embodiment is one kind therein, it can actually change control in several ways
The volume size and shape of chamber processed, such as change the shape of valve pocket 3 upper end to change shapes and sizes of control chamber etc..
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 to move upwards, the second damping hole 9 is opened, and the pressure of control chamber 10 declines, hydraulic fluid port B and control
The differential pressure action of chamber 10 is on main valve plug 4.Voltage on scaling up electromagnet 1, hydraulic fluid port B and the pressure difference of control chamber 10 increase,
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, first
Area of passage between the damping hole 9 of guide valve core 6 and second reaches maximum, and main valve plug 4 fully opens.
In one embodiment, during hydraulic fluid port A oil-feeds, first give proportion electro-magnet 1 one voltages so that so that pilot valve
6 in the position (as shown in Figure 4) for opening the second damping hole 9 completely.Continue the voltage of scaling up electromagnet 1, pilot valve 6
On the area of passage of throttling channel 62 reduce (as shown in Figure 5), main valve plug 4 under the differential pressure action of hydraulic fluid port A and control chamber 10 by
Gradually open.The voltage of further scaling up electromagnet 1, throttling channel 62 separate control chamber 10 and first guide cavity completely, and main valve plug 4 reaches
To maximum opening.
In an embodiment of the present invention, when the drive of armature 7 pilot valve 6 moves up, by controlling proportion electro-magnet 1
Voltage swing can control unlatching, closing and the openings of sizes of the second damping hole 9 and pilot valve throttling channel 62, so as to be formed pair
Hydraulic fluid port A or bidirectional throttle control during 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 (as shown in Figure 2), now the pressure of control chamber 10 will decline, the pressure shape in hydraulic fluid port B pressure and control chamber 10
Into pressure difference, this differential pressure action (due to main valve plug 4 and stairstepping, produces difference in areas) on main valve plug 4, but now makes a concerted effort also
It is not enough to promote main valve plug 4 to rise.
Continue to increase the voltage on proportion electro-magnet 10, the second damping hole 9 is further opened, hydraulic fluid port B pressure and control
Pressure difference increase in chamber 10, main valve plug 4 are begun to move up, and hydraulic fluid port B fluid flows to hydraulic fluid port A (as shown in Figure 3).
Continue to increase the voltage of given proportion electro-magnet 1, the excessively stream between the second damping hole 9 and pilot valve 6
Area reaches maximum, and now main valve plug 4 fully opens.
If hydraulic fluid port A oil-feeds are, it is necessary to first give the enough initial voltages of proportion electro-magnet 1 so that pilot valve 6 is in complete
Open the position (as shown in Figure 4) of the second damping hole 9.On the basis of initial voltage, voltage signal, pilot valve are gradually increased
During 6 gradually rise, the area of passage of pilot valve throttling channel 62 is gradually reduced, and the area of passage of throttling channel 62 is gradually less than
The area of passage of first damping hole 8.So main valve plug 4 is progressively opened in the presence of making a concerted effort, hydraulic fluid port A to hydraulic fluid port B flow by
Gradual change is big.
In accordance with the above, the maximum voltage of proportion electro-magnet 1 is given during hydraulic fluid port A oil-feeds, throttling channel 62 can completely close (such as
Shown in Fig. 5), main valve plug 4 can reach maximum opening, and now hydraulic fluid port A to hydraulic fluid port B flowings are up to maximum stream flow.If do not give ratio
The voltage of electromagnet 1, pilot valve 6 are in the position (as shown in Figure 1) for sealing the second damping hole 9, hydraulic fluid port A to hydraulic fluid port B mobile phases
When in check valve, also reaching maximum stream flow.Therefore, maximal rate control can give proportion electro-magnet 1 by hydraulic fluid port A oil-feeds
Maximum voltage and do not realized to both modes of the non-return valve function of voltage.
In order to better illustrate the effect of the ratio one-way flow valves of the double-direction control of the present invention, as Fig. 6 shows one
Using the principle schematic of the hydraulic system of the ratio one-way flow valves 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 solenoid directional control valve 14 of two-bit triplet must be electric, after commutation
Into the ratio one-way flow valves 15 of the double-direction control of the present invention, in the case of the sufficient initial pressure of proportion electro-magnet 1 is given,
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 be electric, then solenoid directional control valve 14 is operated in the right side
Side position, the fluid of hydraulic cylinder 16 is through hydraulic fluid port B, and in the case where giving 1 corresponding voltage of proportion electro-magnet, fluid is with ratio control
The mode of system flows to hydraulic fluid port A from hydraulic fluid port B, then returns to fuel tank through solenoid directional control valve 14.In the case of this kind, under if desired midway stops
Drop, the dead electricity of ratio one-way flow valves 15 of double-direction control, 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 second damping hole 9,
Unlatching, closing and the openings of sizes of pilot valve throttling channel and main valve plug 4, realization can be achieved with by a proportional directional valve
Bidirectional throttle control during to hydraulic fluid port A or hydraulic fluid port B oil-feeds, thus structure is simpler, cost is lower.
In addition, explanation, core technology of the invention are：Pilot valve 6 and the second damping hole 9 composition first are variable
Throttling, pilot valve throttling channel 62 and the endoporus of main valve plug 4 form the second variable restrictor, hydraulic oil from hydraulic fluid port B flow into hydraulic fluid port A when,
The area of the first variable restrictor is controlled to be more than the area of passage of the first damping hole, main valve plug 4 will be opened slowly, and first can switch political loyalty
The area of stream is bigger, and main valve plug 4 is opened bigger.Hydraulic oil from hydraulic fluid port A flow into hydraulic fluid port B when, control the second variable restrictor face
Product is less than the area of passage of the first damping hole, and main valve plug 4 will be opened slowly, and the area of the second variable restrictor is smaller, main valve plug 4
Unlatching it 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 (6)
- A kind of 1. ratio one-way flow valves 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 less than the diameter of the second damping hole；Pilot valve, its one end are fixedly connected on the other end of the armature, and the other end of pilot valve is slidably arranged in main valve In the endoporus of core, cylinder convex shoulder and inclined-plane are sequentially provided with from top to bottom at corresponding second damping hole of the pilot valve other end, Main valve plug endoporus is separated into the control chamber communicated with the first damping hole and the elder generation communicated with the second damping hole by the cylinder convex shoulder Guide cavity, the inclined-plane can block the second damping hole, and the throttling channel of connection control chamber and first guide cavity, institute are provided with the circular shoulder Throttling channel is stated to be arranged to：When pilot valve moves up, throttling channel opening area is less and less, until closing；When the armature drives the pilot valve movement, by controlling the voltage swing of proportion electro-magnet to control the secondth damping Unlatching, closing and the openings of sizes of hole and pilot valve throttling channel are so as to forming two-way section during to hydraulic fluid port A or hydraulic fluid port B oil-feeds Flow control.
- 2. the ratio one-way flow valves of double-direction control according to claim 1, it is characterised in that the control chamber is by holding in the mouth It is that iron lower surface, the middle part of swivel nut, the top of valve pocket, the upper end of main valve plug and pilot valve are formed, positioned at main valve plug endoporus The chamber of upper end.
- 3. the ratio one-way flow valves of double-direction control according to any one of claim 1 to 2, it is characterised in that described One end that pilot valve connects the armature is T-type structure, and one end of the armature is provided with the T-type structure with the pilot valve The the first T-shaped hole coordinated, 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 2nd T In the macropore of type hole, the first T-shaped hole connects with the second T-shaped hole.
- 4. the ratio one-way flow valves of double-direction control according to any one of claim 1 to 3, it is characterised in that hydraulic fluid port B During oil-feed, give proportion electro-magnet one voltage, the armature overcomes the active force of the elastic component, drives the pilot valve Motion upwards, the second damping hole 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, 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, Main valve plug fully opens.
- 5. the ratio one-way flow valves of double-direction control according to any one of claim 1 to 4, it is characterised in that hydraulic fluid port A During oil-feed, give proportion electro-magnet one voltage so that pilot valve is in and opens the second damping hole completely, and pilot valve section The area of passage of chute starts the position reduced；Continue the voltage of scaling up electromagnet, the area of passage of the throttling channel in pilot valve reduces, main valve plug hydraulic fluid port A with Gradually opened under the differential pressure action of control chamber；The voltage of further scaling up electromagnet, the throttling channel in pilot valve completely close, and main valve plug reaches maximum opening.
- 6. the ratio one-way flow valves of the double-direction control according to any one of claim 1 to 5, it is characterised in that described Valve pocket is connected with the other end thread seal of the swivel nut, and the lower end of the main valve plug and the junction of the valve pocket are provided with tiltedly Face.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711088829.1A CN107725842B (en) | 2017-11-08 | 2017-11-08 | The ratio one-way flow valves of double-direction control |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711088829.1A CN107725842B (en) | 2017-11-08 | 2017-11-08 | The ratio one-way flow valves of double-direction control |
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| Publication Number | Publication Date |
|---|---|
| CN107725842A true CN107725842A (en) | 2018-02-23 |
| CN107725842B CN107725842B (en) | 2019-05-28 |
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|---|---|---|---|
| CN201711088829.1A Active CN107725842B (en) | 2017-11-08 | 2017-11-08 | The ratio one-way flow valves of double-direction control |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109139591A (en) * | 2018-09-25 | 2019-01-04 | 中国农业大学 | A kind of adaptive pilot-operated type electric-hydraulic proportion screw-in cartridge valve of mountain and hill |
| 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 |
| CN110878777A (en) * | 2019-11-28 | 2020-03-13 | 宁波文泽机电技术开发有限公司 | Pressure control valve |
| CN111720382A (en) * | 2020-06-30 | 2020-09-29 | 潍柴动力股份有限公司 | Load holding valve and hydraulic control system |
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| JP2000009250A (en) * | 1998-06-22 | 2000-01-11 | Kenji Masuda | Proportional throttle valve |
| CN1350125A (en) * | 2001-12-07 | 2002-05-22 | 卢永松 | Hydraulic balancing valve |
| JP2004286159A (en) * | 2003-03-24 | 2004-10-14 | Finesinter Co Ltd | Pilot type solenoid valve |
| DE10343608A1 (en) * | 2003-09-20 | 2005-04-14 | Buchholz Hydraulik Gmbh | Magnetically controlled proportional throttle valve for use with fork lift truck plunger cylinders has pilot piston mounted in axial bore in main piston, conical section at top forming seal with bore when it is closed |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109139591A (en) * | 2018-09-25 | 2019-01-04 | 中国农业大学 | A kind of adaptive pilot-operated type electric-hydraulic proportion screw-in cartridge valve of mountain and hill |
| CN109139591B (en) * | 2018-09-25 | 2020-03-10 | 中国农业大学 | Mountain and hill self-adaptation pilot-operated type electro-hydraulic proportional threaded cartridge 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 |
| CN110878777A (en) * | 2019-11-28 | 2020-03-13 | 宁波文泽机电技术开发有限公司 | Pressure control valve |
| CN111720382A (en) * | 2020-06-30 | 2020-09-29 | 潍柴动力股份有限公司 | Load holding valve and hydraulic control system |
| EP4174349A4 (en) * | 2020-06-30 | 2024-04-03 | Weichai Power Co., Ltd. | Load holding valve and hydraulic control system |
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|---|---|
| CN107725842B (en) | 2019-05-28 |
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