CN206694342U - New Structure Speed Control Valve - Google Patents
New Structure Speed Control Valve Download PDFInfo
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- CN206694342U CN206694342U CN201720398910.9U CN201720398910U CN206694342U CN 206694342 U CN206694342 U CN 206694342U CN 201720398910 U CN201720398910 U CN 201720398910U CN 206694342 U CN206694342 U CN 206694342U
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- valve
- speed control
- control valve
- valve core
- flow
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Abstract
The utility model discloses a kind of New Structure Speed Control Valve, its flow controlled 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, so that decompression valve core is all the time by a constant action of hydraulic force, even if valve core is depressurized due to when position change occurs for feedback effect, also can guarantee that the forward and backward pressure difference of restriction is constant.Meanwhile to ensure that the active area of decompression valve core both ends hydraulic oil is equal, an Area Compensation plunger is provided with the other end of decompression valve core.The utility model overcomes the original inherent shortcoming for using spring reset, ensure that the forward and backward pressure difference of restriction is constant, and in the timing of choke area one, flow through the flow of 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 utility model is related to it is a kind of control fluid flow flow speed control valve technical field, more particularly to a kind of flow 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, load change is only applicable to less or to the less demanding occasion of velocity control accuracy.Known restriction
Pressure flow equation Q=CdA（2ΔP/ρ）1/2Show, it is directly proportional to the aperture area A of restriction to flow through the flow of restriction,
It is directly proportional to the forward and backward pressure differential deltap P of restriction half power, to ensure that flow Q is constant, only it 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 is set 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 composes in parallel.The principle of both valves is overflow using setting difference type pressure-reducing valve and differential pressure type
The valve element movement for flowing valve to change restriction forward and backward pressure difference progress pressure compensation, 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 both ends of core, balanced by the difference of the elastic force and hydraulic power of hydraulic thrust caused by pressure difference and spring, i.e. hydraulic pressure caused by pressure difference
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 are certain.When the outlet pressure of restriction changes with load, 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
Small carry out pressure compensation, setting difference type decompression valve core is set to be moved to a new equilbrium position steady operation, before ensureing restriction,
Pressure difference is basically unchanged afterwards.Consider in structure after taking balanced measure to hydraulic power, 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 hydraulic pressure caused by setting difference type decompression valve core both ends
Thrust is equal to the elastic force of spring, therefore the pressure difference at setting difference type decompression valve core both ends is equal to elastic force divided by the setting difference type decompression of spring
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 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 depressurize the change in location of valve core with setting difference type and change.Therefore, the pressure difference at setting difference type decompression valve core both 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 causes in structure
Force variation, but it is constant to cannot guarantee that the forward and backward pressure difference of restriction is stablized.Known overflow throttle valve similarly cannot guarantee that
The forward and backward pressure difference of restriction is stablized constant.Therefore, extra high occasion, existing flow speed control valve and overflow are required in velocity control accuracy
The performance of choke valve can not just meet its requirement, therefore design a kind of flow completely not the New Structure Speed Control Valve influenceed by load change
It is particularly important.
The content of the invention
The purpose of this utility model is insufficient existing for existing speed governing valve technology in order to overcome, there is provided a kind of new speed governing
Valve, in entrance throttle governing circuit loop and by-pass throttle speed control loop, its flow controlled not to be completely by the shadow of load change
Ring, to ensure that it is constant that hydraulic cylinder speed is stablized.
In order to solve the above technical problems, the utility model adopts the following technical scheme that：New Structure Speed Control Valve is in existing speed governing
On the basis of valve, a reset plunger for making valve core reset is set to replace original reset bullet at the big end of decompression valve core
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 begins
Eventually by a hydraulic action, even if decompression valve core changes because position occurs for feedback effect, its reset plunger end is made
Thrust P1 × B is also constant all the time caused by hydraulic oil P1, and B is reset plunger end cross-sectional area.Simultaneously in pressure-reducing valve valve
The small end termination of core sets an Area Compensation plunger, the cross-sectional area of Area Compensation plunger and the cross-sectional area phase of reset plunger
Deng, 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, depressurizes big the end chamber and flow speed control valve of valve core
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, and the cross-sectional area of Area Compensation plunger is with answering
The cross-sectional area of position plunger is equal, to ensure the area equation of decompression valve core pressure at two ends oil P2, P3 effect.
Above-mentioned Area Compensation plunger end chamber is connected by drain path with fuel tank.
The utility model has the advantage that compared with prior art：Because original structure uses spring reset, its pressure-reducing valve
When carrying out pressure feedback, spool position is changed, and causes the elastic force of its back-moving spring to be changed, so pressure-reducing valve
The pressure difference at valve element both ends is also changed.And after using New Structure Speed Control Valve structure of the present utility model, overcome original use
The inherent shortcoming of spring reset, 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 position change, can also ensure that the hydraulic thrust of reset plunger end is constant when carrying out pressure feedback, with
Ensure that the forward and backward pressure difference of restriction is constant, when the timing of opening degree one of restriction, the flow for flowing through flow speed control valve is not become by load completely
Changing influences, so as to ensure that the velocity control accuracy of hydraulic cylinder.
Brief description of the drawings
Fig. 1 is the utility model structure working principle figure.
In Fig. 1 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- subtract
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 end termination effective active area A3,14- emptying passages, 15- Area Compensation plungers, 16- areas benefit
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 after the decompression of P2- pressure-reducing valves valve port, P3- flow speed control valve oil-out pressures
Power.
Embodiment
The technical solution of the utility model 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 are 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 acts on multiple
In the area B of the position termination of plunger 7；Another way pressure after the pressure-reducing valve valve port decompression that opening degree is h1 is reduced to P2, P2 warp knuckles again
Flowed out after stream valve valve port, pressure is reduced to P3, and 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 be A2, and pressure oil P3 guides to that to depressurize valve core big through oilhole 1
Hold on active area A1, the stress balance equation for depressurizing valve core is：
P3×A1+P1×B=P2(A2+A3)+Fs
Fs is the hydraulic power suffered by decompression 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.Due to pressure oil P1, by the overflow valve of hydraulic pump outlet to be adjusted to definite value constant, area B,
A1 be constant it is constant, therefore P2-P3 completely by（P1×B）/ A1 is defined as certain value, if now the opening degree h2 of restriction is not yet
Become, then the flow for flowing through restriction is also certain value, ensure 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 load it is invariable when, the pressure P3 of flow speed control valve oil-out 22 is not
Become, the inlet pressure P1 of flow speed control valve is adjusted to that definite value is constant by the overflow valve of pump discharge, and the opening degree h1 for depressurizing valve core 9 is automatic
When being adjusted to meet pressure flow equilibrium equation, decompression valve core 9 is also stablized not in an equilbrium position steady operation, now P2
Become, thus according to the stress balance equation of valve element obtain P2-P3=（P1×B-Fs）/ A1, using Fs=0 after hydraulic power balanced measure, institute
With P2-P3=（P1×B）/A1.Because now orifice openings degree h2 is constant, the forward and backward pressure difference P2-P3 of restriction is also constant, therefore
Flow through that the flow of restriction is constant, the hydraulic cylinder speed of guarantee is stablized 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, because 9 original stress balance of decompression valve core has been broken in P3 rises, decompression valve core 9 increases to valve port
Big direction movement, pressure-reducing valve valve port degree h1 increases, its depressurization weaken, and cause 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 and the first situation are just the same, and when the load that ensure that increases, the forward and backward pressure difference of restriction is invariable,
If now the opening degree h2 of restriction is constant, it is constant to flow through the flow of restriction, ensure that hydraulic cylinder speed increases in load
When still stablize it is 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, broken 9 original stress balance of decompression valve core because P3 is reduced, decompression valve core 9 is to opening
The direction movement that mouth reduces, pressure-reducing valve valve port degree h1 reduce, and the enhancing of its depressurization, cause 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 and the first and second of situation are just the same, when ensure that load reduces, the forward and backward pressure of restriction
Difference is invariable, if now the opening degree h2 of restriction is constant, it is constant to flow through the flow of restriction, ensure that hydraulic cylinder speed
Still stablize when loading and reducing constant.
In summary, change regardless of load, New Structure Speed Control Valve can ensure that the forward and backward pressure difference of restriction is constant, save
After head piece opening degree h2 is set up, flow through that the flow of restriction is constant, ensure 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 are 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 |
|---|---|---|---|
| CN201720398910.9U CN206694342U (en) | 2017-04-17 | 2017-04-17 | New Structure Speed Control Valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720398910.9U CN206694342U (en) | 2017-04-17 | 2017-04-17 | New Structure Speed Control Valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN206694342U true CN206694342U (en) | 2017-12-01 |
Family
ID=60445131
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201720398910.9U Expired - Fee Related CN206694342U (en) | 2017-04-17 | 2017-04-17 | New Structure Speed Control Valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN206694342U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106907367A (en) * | 2017-04-17 | 2017-06-30 | 西华大学 | New Structure Speed Control Valve |
| CN107906230A (en) * | 2017-12-21 | 2018-04-13 | 宁波文泽机电技术开发有限公司 | A kind of two-way one-way speed-regulating valve |
| CN108488455A (en) * | 2018-04-11 | 2018-09-04 | 王爱菊 | Valve gear and hydraulic system |
| CN108612692A (en) * | 2018-05-14 | 2018-10-02 | 江苏理工学院 | Dual spring pressure compensation speed governing valve |
-
2017
- 2017-04-17 CN CN201720398910.9U patent/CN206694342U/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106907367A (en) * | 2017-04-17 | 2017-06-30 | 西华大学 | New Structure Speed Control Valve |
| CN107906230A (en) * | 2017-12-21 | 2018-04-13 | 宁波文泽机电技术开发有限公司 | A kind of two-way one-way speed-regulating valve |
| CN107906230B (en) * | 2017-12-21 | 2019-06-18 | 大庆丹枫石油技术开发有限公司 | A kind of two-way one-way speed-regulating valve |
| CN108488455A (en) * | 2018-04-11 | 2018-09-04 | 王爱菊 | Valve gear and hydraulic system |
| CN108612692A (en) * | 2018-05-14 | 2018-10-02 | 江苏理工学院 | Dual spring pressure compensation speed governing valve |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20171201 Termination date: 20180417 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |