CN106907367A - New Structure Speed Control Valve - Google Patents
New Structure Speed Control Valve Download PDFInfo
- Publication number
- CN106907367A CN106907367A CN201710248694.4A CN201710248694A CN106907367A CN 106907367 A CN106907367 A CN 106907367A CN 201710248694 A CN201710248694 A CN 201710248694A CN 106907367 A CN106907367 A CN 106907367A
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- Prior art keywords
- speed control
- valve
- control valve
- valve core
- plunger
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a kind of New Structure Speed Control Valve, the flow of its control is not influenceed by load change completely, solves velocity-stabilization sex chromosome mosaicism of the hydraulic cylinder in the case of varying load.Its principle is on the basis of existing flow speed control valve, a reset plunger is set to replace original back-moving spring, and the pressure oil of flow speed control valve oil inlet is guided into reset plunger end chambers by oilhole two, so that decompression valve core receives a constant action of hydraulic force all the time, even if decompression valve core changes because feedback effect occurs position, the thrust that the hydraulic oil of its reset plunger end effect is produced is also constant all the time, it is ensured that the forward and backward pressure difference of restriction is constant.Meanwhile, for the active area for ensureing decompression valve core two ends hydraulic oil is equal, one Area Compensation plunger being set in the other end of decompression valve core, the cross-sectional area of Area Compensation plunger is equal with the cross-sectional area of reset plunger.Instant invention overcomes the original inherent shortcoming using spring reset, it is ensured that the forward and backward pressure difference of restriction is constant, in the timing of choke area one, the flow for flowing through flow speed control valve is not influenceed by load change completely, so as to ensure that the velocity control accuracy of hydraulic cylinder.
Description
Technical field
The present invention relates to a kind of flow speed control valve technical field of control fluid flow, more particularly to a kind of flow is not with load
The New Structure Speed Control Valve of change.
Background technology
To control the movement velocity of hydraulic cylinder, choke valve is a kind of most simple and most basic flow control valve, but due to
The poor rigidity of choke valve, is only applicable to load change less or to the less demanding occasion of velocity control accuracy.Known restriction
Pressure flow equation Q=CdA（2ΔP/ρ）1/2Show, flow through the flow of restriction and be directly proportional to the aperture area A of restriction,
Two/first power to the forward and backward pressure differential deltap P of restriction is directly proportional, constant to ensure flow Q, only need to ensure that A and Δ P are constant
.Therefore, to solve the velocity-stabilization sex chromosome mosaicism that load changes big hydraulic cylinder, after the aperture area A of restriction sets up,
Should take measures proof load change when, the forward and backward pressure difference of choke valve valve port is constant.
The flow speed control valve that the currently known useful choke valve of technology and setting difference type pressure-reducing valve are composed in series, and with choke valve and
The overflow throttle valve that differential pressure type overflow valve is composed in parallel.The principle of both valves is overflow using setting difference type pressure-reducing valve and differential pressure type
Flow the valve element movement of valve to carry out pressure compensation to the forward and backward pressure difference change of restriction, to ensure the forward and backward pressure difference of choke valve valve port
It is basically unchanged.
It can be seen from known flow speed control valve, its principle is that the forward and backward pressure oil of restriction is guided into setting difference type pressure-reducing valve valve respectively
The two ends of core, the hydraulic thrust and the elastic force of spring and the difference of hydraulic power produced by pressure difference is balanced, i.e., the hydraulic pressure that pressure difference is produced
The elastic force that thrust is equal to spring subtracts hydraulic power.Such as load it is invariable, setting difference type decompression valve core it is steady an equilbrium position
Fixed work, setting difference type pressure-reducing valve valve core opening degree is certain.When the outlet pressure of restriction is with load change, setting difference type pressure-reducing valve
Valve element stress balance is broken, valve element movement, depressurizes valve core movement by setting difference type to change the big of pressure relief valve port opening degree
It is small to carry out pressure compensation, setting difference type decompression valve core is moved to a new equilbrium position steady operation, it is ensured that before restriction,
Pressure difference is basically unchanged afterwards.After considering to take balanced measure to hydraulic power in structure, it is believed that act on setting difference type pressure-reducing valve valve
Hydraulic power on core is zero.Therefore, the forward and backward pressure of restriction is respectively acting on the hydraulic pressure that setting difference type decompression valve core two ends produce
Thrust is equal to the elastic force of spring, therefore the elastic force that the pressure difference at setting difference type decompression valve core two ends is equal to spring depressurizes divided by setting difference type
The effective active area of valve core.Although the effective active area of setting difference type decompression valve core is certain value, it is surely poor to act on
The elastic force of the spring on formula decompression valve core is not to immobilize, and its elastic force is relevant with the decrement of spring, and the pressure of spring
Contracting amount can change with the change in location of setting difference type decompression valve core.Therefore, the pressure difference at setting difference type decompression valve core two ends also can
Change, the i.e. forward and backward pressure difference of restriction can change.Although it is contemplated that being reduced using slinky spring because spool displacement is caused in structure
Force variation, but cannot guarantee that the forward and backward pressure difference of restriction stablizes constant.Known overflow throttle valve similarly cannot guarantee that
The forward and backward pressure difference of restriction stablizes constant.Therefore, in the velocity control accuracy extra high occasion of requirement, existing flow speed control valve and overflow
The performance of choke valve cannot just meet its requirement, therefore the New Structure Speed Control Valve that a kind of flow of design is not influenceed by load change completely is just
It is particularly important.
The content of the invention
The invention aims to overcome the shortcomings of that existing speed governing valve technology is present, there is provided a kind of New Structure Speed Control Valve, use
In entrance throttle governing circuit loop and by-pass throttle speed control loop, the flow of its control is not influenceed by load change completely, with
Ensure that hydraulic cylinder speed is stablized constant.
In order to solve the above technical problems, the present invention is adopted the following technical scheme that：New Structure Speed Control Valve is in existing flow speed control valve
On the basis of, the big end of decompression valve core set one make valve core reset with reset plunger come instead of original back-moving spring,
And the pressure oil P1 of flow speed control valve oil inlet is guided into reset plunger end chambers by oilhole two, so that decompression valve core is received all the time
One hydraulic action, even if decompression valve core changes because feedback effect occurs position, the effect of its reset plunger end
Thrust P1 × B that hydraulic oil P1 is produced is also constant all the time, and B is reset plunger end cross-sectional area.Simultaneously in decompression valve core
Small end termination sets an Area Compensation plunger, and the cross-sectional area of Area Compensation plunger is equal with the cross-sectional area of reset plunger,
And Area Compensation plunger end chamber is connected by drain path with fuel tank.
Above-mentioned reset plunger is arranged on the large end face of decompression valve core, big end chamber and the flow speed control valve of the valve core that depressurizes
Oil-out is communicated, and reset plunger end chambers are communicated by oilhole two with flow speed control valve oil inlet.
Above-mentioned Area Compensation plunger is arranged on decompression valve core small end termination, the cross-sectional area of Area Compensation plunger with it is multiple
The cross-sectional area of position plunger is equal, to ensure the area equation that decompression valve core pressure at two ends oil P2, P3 are acted on.
Above-mentioned Area Compensation plunger end chamber is connected by drain path with fuel tank.
The present invention has the advantage that compared with prior art：Because original structure uses spring reset, its pressure-reducing valve is entering
Spool position there occurs change during row pressure feedback, cause the elastic force of its back-moving spring to there occurs change, so decompression valve core
The pressure difference at two ends also there occurs change.And after using New Structure Speed Control Valve structure of the invention, overcome and used spring reset originally
Inherent shortcoming, make to act on a constant hydraulic thrust in the reset plunger of pressure-reducing valve spool end all the time, even if relief pressure valve cartridge
There occurs that position changes when pressure feedback is carried out, can also ensure that the hydraulic thrust of reset plunger end is constant, to ensure throttling
The forward and backward pressure difference of mouth is constant, and when the timing of opening degree one of restriction, the flow for flowing through flow speed control valve is not influenceed by load change completely,
So as to ensure that the velocity control accuracy of hydraulic cylinder.
Brief description of the drawings
Accompanying drawing is structure working principle figure of the present invention.
Wherein shown in label：1- valve bodies, 2- oilholes one, big end active area A1, the 4- reset plunger end of 3- decompression valve cores
Portion's chamber, 5- reset plunger end cross-sectional area B, 6- oilhole two, 7- reset plungers, the 8- decompression big end chambers of valve core, 9- subtracts
Pressure valve valve element, 10- decompression valve core small end effective active area A2,11- decompression valve core small end chambers, 12- flow speed control valve oil-feeds
Mouthful, 13- decompression valve core small ends termination effective active area A3,14- emptying passage, 15- Area Compensation plungers, 16- areas are mended
Repay plunger end chamber, 17- decompression valve core small ends termination chamber, 18- oilholes three, 19- throttle valve adjustment screws, 20- throttlings
Valve core, 21- oilholes four, 22- flow speed control valve oil-outs, 23- throttle valve springs, h1- pressure-reducing valve valve port degree, h2- choke valves
Valve port degree, P1- flow speed control valve inlet pressures, oil liquid pressure, P3- flow speed control valve oil-out pressures after the decompression of P2- pressure-reducing valves valve port
Power.
Specific embodiment
Technical scheme is further described below in conjunction with the accompanying drawings.
Referring to shown in accompanying drawing, New Structure Speed Control Valve includes setting difference type pressure-reducing valve and choke valve, the two series connection, setting difference type pressure-reducing valve
Preceding, choke valve is rear.The big end of decompression valve core 9 is provided with a reset plunger 7, and there is a reset plunger termination of reset plunger 7
End chambers 4, its effective active area is B, and the pressure oil P1 of hydraulic pump output flows into New Structure Speed Control Valve after overflow valve voltage stabilizing
Oil inlet 12.Pressure oil P1 punishes two-way in entrance, guides to reset plunger end chambers 4 through oilhole 26 all the way, and act on multiple
In the area B of the position termination of plunger 7；Pressure is reduced to P2 after another road is depressurized through opening degree for the pressure-reducing valve valve port of h1, P2 warp knuckles again
Flowed out after stream valve valve port, pressure is reduced to P3, P3 connects hydraulic cylinder band dynamic load.Pressure oil P2 is through oilhole 3 18 and oilhole 4 21 simultaneously
Decompression valve core small end termination chamber 17 and decompression valve core small end chamber 11 are guided to respectively, and decompression valve core small end termination is effective
Active area is A3, and decompression valve core small end effective active area is A2, and it is big that pressure oil P3 guides to decompression valve core through oilhole 1
Hold on active area A1, the stress balance equation of the valve core that depressurizes is：
P3×A1+P1×B=P2(A2+A3)+Fs
Fs is the hydraulic power depressurized suffered by valve core；
By A1=A2+A3, arrange above formula and obtain：
P2-P3=（P1×B-Fs）/A1
P2-P3 is the forward and backward pressure difference of restriction, if using hydraulic power balanced measure in structure, can make Fs=0, therefore：
P2-P3=（P1×B）/A1.Because pressure oil P1 is adjusted to by the overflow valve of hydraulic pump outlet, definite value is constant, and area B, A1 are
Constant is constant, thus P2-P3 completely by（P1×B）/ A1 is defined as certain value, if now the opening degree h2 of restriction is also constant,
The flow for flowing through restriction is also certain value, it is ensured that the velocity-stabilization of hydraulic cylinder is constant.
Divide three kinds of loading condition explanation decompression specific compensation process of valve core below：
The first：Orifice openings degree h2 is certain, and when loading invariable, the pressure P3 of flow speed control valve oil-out 22 is constant, adjusts
The inlet pressure P1 of fast valve is adjusted to that definite value is constant by the overflow valve of pump discharge, the opening degree h1 adjust automaticallies of the valve core 9 that depressurizes
When pressure flow equilibrium equation is met, decompression valve core 9 also stablizes constant in an equilbrium position steady operation, now P2,
Therefore P2-P3=is obtained according to the stress balance equation of valve element（P1×B-Fs）/ A1, using Fs=0 after hydraulic power balanced measure, so
P2-P3=（P1×B）/A1.Because now orifice openings degree h2 is constant, forward and backward pressure difference P2-P3 is also constant for restriction, therefore flows through
The flow of restriction is constant, it is ensured that hydraulic cylinder speed stablize constant.
Second：In the first situation（I.e. valve element is in a certain position stress balance）On the basis of, if now load increase,
Cause P3 pressure rises, the original stress balance of decompression valve core 9 has been broken because P3 is raised, decompression valve core 9 increases to valve port
Big direction movement, pressure-reducing valve valve port degree h1 increases, its depressurization weakens, and causes P2 to increase, when P2 increases to satisfaction
P2-P3=（P1×B）During/A1, decompression valve core 9 reaches stress balance a new position, again steady operation, now P2-
P3=（P1×B）/ A1 is just the same with the first situation, it is ensured that load increase when, the forward and backward pressure difference of restriction is invariable,
If now the opening degree h2 of restriction is constant, the flow for flowing through restriction is constant, it is ensured that hydraulic cylinder speed increases in load
When still stablize constant.
The third：Similarly, in the first situation（I.e. valve element is in a certain position stress balance）On the basis of, if now loading
Reduce, cause the reduction of P3 pressure, because the original stress balance of decompression valve core 9 has been broken in P3 reductions, decompression valve core 9 is to opening
The direction movement that mouth reduces, pressure-reducing valve valve port degree h1 reduces, and the enhancing of its depressurization causes P2 to reduce, when P2 is reduced to
Meet P2-P3=（P1×B）During/A1, decompression valve core 9 reaches stress balance a new position, again steady operation, this
When P2-P3=（P1×B）/ A1 is just the same with the first and second situation, it is ensured that when load reduces, the forward and backward pressure of restriction
Difference is invariable, if now the opening degree h2 of restriction is constant, the flow for flowing through restriction is constant, it is ensured that hydraulic cylinder speed
Still stablize constant when loading and reducing.
In sum, no matter how load changes, and New Structure Speed Control Valve can ensure that the forward and backward pressure difference of restriction is constant, in section
After head piece opening degree h2 sets up, the flow for flowing through restriction is constant, it is ensured that stablizing for hydraulic cylinder speed is constant.
Claims (3)
1. New Structure Speed Control Valve, including the setting difference type pressure-reducing valve and choke valve being serially connected, it is characterised in that：In decompression valve core
One reset plunger is set on large end face, and reset plunger end chambers are communicated by oilhole two with flow speed control valve oil inlet.
2. New Structure Speed Control Valve according to claim 1, it is characterised in that：Decompression valve core small end termination is provided with Area Compensation
Plunger, the cross-sectional area of Area Compensation plunger is equal with the cross-sectional area of reset plunger.
3. New Structure Speed Control Valve according to claim 2, it is characterised in that：Area Compensation plunger end chamber passes through drain path
Connected with fuel tank.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710248694.4A CN106907367A (en) | 2017-04-17 | 2017-04-17 | New Structure Speed Control Valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710248694.4A CN106907367A (en) | 2017-04-17 | 2017-04-17 | New Structure Speed Control Valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106907367A true CN106907367A (en) | 2017-06-30 |
Family
ID=59210656
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710248694.4A Pending CN106907367A (en) | 2017-04-17 | 2017-04-17 | New Structure Speed Control Valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106907367A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108131346A (en) * | 2017-12-21 | 2018-06-08 | 宁波文泽机电技术开发有限公司 | A kind of threeway one-way speed-regulating valve |
| CN108413085A (en) * | 2018-05-22 | 2018-08-17 | 重庆邮电大学 | A kind of pressure-relief one-way valve |
| CN111997956A (en) * | 2020-08-13 | 2020-11-27 | 邵延荣 | Hydraulic speed regulating valve |
| CN112762206A (en) * | 2021-01-18 | 2021-05-07 | 大连大学 | Speed regulating valve with pressure reducing and throttling double adjusting functions |
| CN115419626A (en) * | 2022-09-14 | 2022-12-02 | 哈尔滨理工大学 | Novel hydraulic valve with structure for preventing oil inlet and outlet of pressure regulator from being blocked |
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| US3556135A (en) * | 1968-07-10 | 1971-01-19 | Mitsubishi Heavy Ind Ltd | Automatic flow control valve |
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| US5280804A (en) * | 1991-04-01 | 1994-01-25 | Mitsubihi Jukogyo Kabushiki Kaisha | Control valve |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108131346A (en) * | 2017-12-21 | 2018-06-08 | 宁波文泽机电技术开发有限公司 | A kind of threeway one-way speed-regulating valve |
| CN108413085A (en) * | 2018-05-22 | 2018-08-17 | 重庆邮电大学 | A kind of pressure-relief one-way valve |
| CN108413085B (en) * | 2018-05-22 | 2020-02-07 | 重庆邮电大学 | Pressure reducing one-way valve |
| CN111997956A (en) * | 2020-08-13 | 2020-11-27 | 邵延荣 | Hydraulic speed regulating valve |
| CN112762206A (en) * | 2021-01-18 | 2021-05-07 | 大连大学 | Speed regulating valve with pressure reducing and throttling double adjusting functions |
| CN115419626A (en) * | 2022-09-14 | 2022-12-02 | 哈尔滨理工大学 | Novel hydraulic valve with structure for preventing oil inlet and outlet of pressure regulator from being blocked |
| CN115419626B (en) * | 2022-09-14 | 2024-09-20 | 哈尔滨理工大学 | Novel hydraulic valve with anti-blocking structure for oil inlet and outlet of pressure regulator |
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Application publication date: 20170630 |