CN2846835Y - Pressure flow electrohydraulic servo valve - Google Patents
Pressure flow electrohydraulic servo valve Download PDFInfo
- Publication number
- CN2846835Y CN2846835Y CN 200520097282 CN200520097282U CN2846835Y CN 2846835 Y CN2846835 Y CN 2846835Y CN 200520097282 CN200520097282 CN 200520097282 CN 200520097282 U CN200520097282 U CN 200520097282U CN 2846835 Y CN2846835 Y CN 2846835Y
- Authority
- CN
- China
- Prior art keywords
- feedback
- valve
- pressure
- guiding valve
- control
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Landscapes
- Servomotors (AREA)
Abstract
The utility model relates to a pressure flow electrohydraulic servo valve. The utility model is characterized in that a twin flapper-and-nozzle valve is connected with a force feedback centering slide valve control chamber by an oil path, and the feedback centering slide valve with load pressure is respectively connected with a hydraulic oil and a load two-chamber oil gallery by the oil path; a fixed orifice is arranged on the controlling oil path of the hydraulic oil which extends to the twin flapper-and-nozzle valve. The valve ensures sufficient stability margin of the electro-hydraulic position servo system which is under damping and has resonant load, and the utility model enhances the quality and the performance of products. Therefore, the utility model is widely applied to various electrohydraulic loading servo-control systems.
Description
Technical field
The utility model relates to a kind of existing higher power control requirement that is applicable to, the electric liquid that has higher positioning control to require again loads the pressure flow electrohydraulic control of servo-control system.Belong to the electrohydraulic servo-controlling system technical field.
Background technique
In the electric liquid loading system in modern times, be that electricity consumption flow quantity servovalve comes control loaded power comparatively at large, though this system also can realize composing loading of task by predetermined load, but because the output of the pressure of electric flow quantity servovalve is nonlinear characteristic, loading system is existed disturb greatly, control difficulty height, the system design complexity, control accuracy is low, and accuracy be difficult for to guarantee, redundant force defective such as remove difficulties.The system that has improves loading accuracy and loads rapidity in order to remove redundant force, has to control little executive component with large-capacity valve; The system that also has obtains big flow gain coefficient and little Pressure gain coefficient, has to big positive opening guiding valve or sets up leakage way.Thereby strengthened oil sources power, caused the waste of the energy.In recent years,, not only require the flow output of valve to be linear, and to require the pressure output of valve also be linear along with electric liquid loads servo-system application more and more widely, also more and more higher to the requirement of the control accuracy of valve and quality.
Electrohydraulic control is the key element of electrohydraulic servo-controlling system, and its performance is very big to the properties influence of system.The electrohydraulic servo-controlling system little for big, the outer load of inertia and load change is big, the damping that improves system is the effective ways of strengthening system stability.Induced pressure changes with system dynamics, and when system resonance aggravated, induced pressure increased and the output no load discharge reduces, if on position feedback type servovalve, increase the induced pressure feedback, then induced pressure and output no load discharge all with the proportional relation of signal code.The pressure flow electrohydraulic control combines the effect of pressure control and flow control, higher power control is provided can for the power system, can provide higher positional accuracy control to position system again, effective damping characteristic is provided can also for high resonant load servo-system.In addition, load in the servo-system at electric liquid, especially can effectively suppress redundant force in passive loading system, resolution system power branch is striven.Therefore the pressure flow electrohydraulic control is that various electric liquid load the major control element in the servo-control system, along with developing rapidly of automatic technology, is with a wide range of applications in fields such as Aeronautics and Astronautics, automobile, metallurgy, machinery.
At present, domestic common servovalve is many with the flow servovalve generally, does not still have the pressure flow electrohydraulic control.Load in servo-control system and the high resonant load electrohydraulic servo-controlling system at various electric liquid, high-quality pressure flow electrohydraulic control can only rely on import.And external existing pressure flow control technique is on the basis of spring balancing flow electrohydraulic control, introduces the pressure flow loop, and it is comprehensive to carry out pressure feedback at the power stage guiding valve.Stable situation lower spring power and feedback hydraulic power make a concerted effort and the control hydraulic coupling balances each other, make the power stage guiding valve obtain a corresponding equilibrium position.The valve quality of this structure is low, poor performance.The frequency range of valve makes the frequency range of valve not high owing to limit by the rigidity of balance spring dynamically the time.The issuable lateral force of balance spring also can make the sensitivity of valve reduce.This structure can not satisfy the requirement that high-quality electric liquid loads servo-system, therefore fails to apply in industrial system preferably.
Summary of the invention
The utility model provides a kind of at above-mentioned deficiency and is applicable to electric liquid Loading Control servo-control system and high resonant load electrohydraulic servo-controlling system, and the pressure flow electrohydraulic control with higher dynamic response capability and high static control accuracy.
The technological scheme that its technical problem that solves the utility model adopts is: a kind of pressure flow electrohydraulic control, comprise the force feedback centering guiding valve of valve body, dry type permanent magnetic torque motor, twin flapper-and-nozzle valve, fixed orifice, floating bushing, bringing onto load pressure feedback and connect oil circuit, it is characterized in that: twin flapper-and-nozzle valve (4) connects with force feedback centering guiding valve (7) control chamber of bringing onto load pressure feedback through oil circuit; The force feedback centering guiding valve (7) of bringing onto load pressure feedback links with high pressure oil, load two chambeies and oil return respectively through oil circuit, and is provided with fixed orifice (9) in high pressure oil leads to the control oil channel of twin flapper-and-nozzle valve; Force feedback centering guiding valve is as power stage, and it links by feedback rod (6), baffle plate (5), control coil and armature component (3); Isolation between force feedback centering guiding valve control chamber and induced pressure feedback cavity is realized by floating bushing (8); Load two chambeies connect with the force feedback centering guiding valve two ends feedback cavity of bringing onto load pressure feedback through the pressure feedback oil circuit, this feedback oil circuit both can be placed on the induced pressure feedback four port valve, can be placed in again outside the induced pressure feedback four port valve, can realize that all the induced pressure feedback carries out comprehensively in power guiding valve level.
The utility model is owing to set up induced pressure feedback on existing force feedback electrohydraulic control basis, corresponding one by one at the delivery pressure difference that has also realized valve one to one simultaneously of the unloaded output flow of having realized valve and input current and input current.Thereby have good pressure, flow linear performance, can directly use linear control theory, simplified system design and analysis the dicyclo control system of power ring and position ring.In addition, the Pressure gain of pressure flow servovalve is smooth, and is adjustable, helps multichannel control and redundancy management The Application of Technology, helps the coherence request in the multichannel control, overcomes the power branch and strives problem.
The utility model can guarantee the stability margin that system is enough to the electro-hydraulic position servo system of underdamping, band resonant load, effectively improves system quality; To power system or loading servo-system, can effectively suppress redundant force, be of value to elimination power branch and strive.
Description of drawings
Fig. 1 is a structural representation of the present utility model.
Figure-1. dry type permanent magnetic torque motor, 2. loam cake, 3. control coil and armature component, 4. flapper valve, 5. baffle plate, 6. feedback rod, 7. guiding valve, 8. floating bushing, 9. throttle orifice, 10. valve body.
Embodiment
As shown in Figure 1, the utility model mainly is made of force feedback centering guiding valve (7), floating bushing (8), fixed orifice (9), valve body (10) and the connection oil circuit of dry type permanent magnetic torque motor (1), loam cake (2), twin flapper-and-nozzle valve (4), bringing onto load pressure feedback.Dry type permanent magnetic torque motor (1) is made up of permanent magnet, control coil and armature component (3) again.Twin flapper-and-nozzle valve (4) is made up of baffle plate (5) and pair of control nozzle as preamplifier stage.The force feedback centering guiding valve (7) of bringing onto load pressure feedback is as power stage, and it links by feedback rod (6), baffle plate (5), control coil and armature component (3).The fixed orifice (9) of on high pressure oil and oil circuit that twin flapper-and-nozzle valve (4) links, having connected respectively.Load two chamber P1, P2 link with force feedback centering guiding valve (7) two ends feedback cavity Pf1, the Pf2 of bringing onto load pressure feedback respectively through oil circuit.
If the electrical signal of system's input makes dry type permanent magnetic torque motor (1) produce clockwise electromagnetic torque, control coil and armature component (3) are under the effect of electromagnetic torque and spring torque, clockwise direction deflection one angle, right end clearance increases so the left gap of twin flapper-and-nozzle valve (4) reduces, then the pilot pressure Pn1 by fixed orifice (9) increases, Pn2 reduces, the force feedback centering guiding valve (7) that promotes the bringing onto load pressure feedback moves to right, high pressure oil Ps enters load cavity p1, and load cavity p2 is back to pr.Meanwhile, force feedback centering guiding valve (7) two ends feedback cavity Pf1, the Pf2 of bringing onto load pressure feedback communicates with load cavity p1, load cavity p2 and experiences the effect of load feedback pressure, stops the force feedback centering guiding valve (7) of bringing onto load pressure feedback to move right.In addition because the skew of the force feedback centering guiding valve (7) of bringing onto load pressure feedback makes feedback rod (6) produce resiliently deformable, and the anticlockwise spring countertorque of baffle plate (5) is given in effect, make during baffle plate returns.When acting on that twin flapper-and-nozzle valve (4) is gone up because the electromagnetic torque that dry type permanent magnetic torque motor (1) produces, when the many moments such as countertorque on the feedback rod (6) reach balance, force feedback centering guiding valve (7) stop motion of bringing onto load pressure feedback, obtain an equilibrium position, the induced pressure of servovalve output this moment and no load discharge all with the proportional relation of current input signal.If induced pressure is owing to interference effect increases, the feedback force of induced pressure feedback effect on the force feedback centering guiding valve (7) of bringing onto load pressure feedback also increases so, destroyed the equalising torque of the force feedback centering guiding valve (7) of bringing onto load pressure feedback, the force feedback centering guiding valve (7) of bringing onto load pressure feedback is moved to the left, control nozzle chambers Pn1 is increased, and Pn2 reduces, and the force feedback centering guiding valve (7) that promotes the bringing onto load pressure feedback moves right and is back to original position.If induced pressure reduces owing to disturbing, its adjustment process is with last opposite.As seen, when input electrical signal was constant, the output flow of valve and output pressure reduction remained unchanged, and the unloaded output flow of input signal and valve and the proportional relation of output loading pressure reduction.Therefore, the utility model can provide system effective additional damping, satisfies the needs of system quality.Particularly load in the servo-system, can effectively suppress redundant force, obtain desirable effect at passive electric liquid.
Claims (4)
1. pressure flow electrohydraulic control, be made up of valve body, dry type permanent magnetic torque motor, twin flapper-and-nozzle valve, the force feedback centering guiding valve of bringing onto load pressure feedback, floating bushing, fixed orifice, it is characterized in that: twin flapper-and-nozzle valve (4) connects with force feedback centering guiding valve (7) control chamber through oil circuit; The force feedback centering guiding valve (7) of bringing onto load pressure feedback through oil circuit respectively with high pressure oil, load two chambeies and and oil circuit link, lead at high pressure oil on the control oil channel of twin flapper-and-nozzle valve (4) and be provided with fixed orifice (9).
2. a kind of pressure flow electrohydraulic control according to claim 1 is characterized in that: the force feedback centering guiding valve (7) of bringing onto load pressure feedback links by feedback rod (6), baffle plate (5), control coil and armature component (3) as power stage.
3. a kind of pressure flow electrohydraulic control according to claim 1, it is characterized in that: force feedback centering guiding valve (7) the two ends feedback cavity of bringing onto load pressure feedback communicates with load two chambeies respectively through the feedback oil circuit, this feedback oil circuit both can be placed on the force feedback centering guiding valve (7) of bringing onto load pressure feedback, can be placed in again outside the force feedback centering guiding valve (7) of bringing onto load pressure feedback, can realize that all induced pressure feedback carries out comprehensively in power guiding valve level.
4. a kind of pressure flow electrohydraulic control according to claim 1 is characterized in that: floating bushing is used for the control chamber and the feedback cavity of the force feedback centering guiding valve (7) of isolation zone induced pressure feedback.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520097282 CN2846835Y (en) | 2005-07-22 | 2005-07-22 | Pressure flow electrohydraulic servo valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520097282 CN2846835Y (en) | 2005-07-22 | 2005-07-22 | Pressure flow electrohydraulic servo valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2846835Y true CN2846835Y (en) | 2006-12-13 |
Family
ID=37512258
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200520097282 Expired - Lifetime CN2846835Y (en) | 2005-07-22 | 2005-07-22 | Pressure flow electrohydraulic servo valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2846835Y (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102927072A (en) * | 2012-11-22 | 2013-02-13 | 李涛 | Electro-hydraulic servo valve with valve core position detection function |
| CN103453948A (en) * | 2013-09-09 | 2013-12-18 | 中国航空动力机械研究所 | Fuel oil metering device adopting torque motor |
| CN108716489A (en) * | 2018-08-07 | 2018-10-30 | 上海航天控制技术研究所 | A kind of Electric hydraulic pressure servo valve power level structure |
| CN110206937A (en) * | 2019-06-24 | 2019-09-06 | 上海衡拓液压控制技术有限公司 | Eliminate the device that pressure is shaken during pressure servo valve pressure declines |
| CN110388355A (en) * | 2019-07-17 | 2019-10-29 | 北京精密机电控制设备研究所 | A kind of adjustment method improving triplex redundance servo valve fail operation pattern congruity |
-
2005
- 2005-07-22 CN CN 200520097282 patent/CN2846835Y/en not_active Expired - Lifetime
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102927072A (en) * | 2012-11-22 | 2013-02-13 | 李涛 | Electro-hydraulic servo valve with valve core position detection function |
| CN103453948A (en) * | 2013-09-09 | 2013-12-18 | 中国航空动力机械研究所 | Fuel oil metering device adopting torque motor |
| CN108716489A (en) * | 2018-08-07 | 2018-10-30 | 上海航天控制技术研究所 | A kind of Electric hydraulic pressure servo valve power level structure |
| CN108716489B (en) * | 2018-08-07 | 2020-04-10 | 上海航天控制技术研究所 | Power stage structure of electro-hydraulic pressure servo valve |
| CN110206937A (en) * | 2019-06-24 | 2019-09-06 | 上海衡拓液压控制技术有限公司 | Eliminate the device that pressure is shaken during pressure servo valve pressure declines |
| CN110388355A (en) * | 2019-07-17 | 2019-10-29 | 北京精密机电控制设备研究所 | A kind of adjustment method improving triplex redundance servo valve fail operation pattern congruity |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN2846835Y (en) | Pressure flow electrohydraulic servo valve | |
| CN201851415U (en) | Electro-hydraulic servo valve | |
| CN105700347B (en) | A kind of hydraulic motor default capabilities tracking and controlling method containing Hysteresis compensation | |
| CN2775363Y (en) | Dynamic pressure feedback electrohydraulic servo valve | |
| US4362182A (en) | Nozzle force feedback for pilot stage flapper | |
| CN204436910U (en) | A kind of asymmetric hydraulic efficiency servo-valve | |
| CN102720876A (en) | Soft match grinding method for eliminating flow characteristic dead zone of electro-hydraulic servo valve | |
| CN105065361B (en) | Proportional flow unit under compound control of electromagnetic switch valves and proportional throttle valve in parallel | |
| CN108227487B (en) | Switching friction compensation active disturbance rejection control method based on prediction model and motion platform | |
| Fadel et al. | Modeling, simulation and control of a fly-by-wire flight control system using classical PID and modified PI-D controllers | |
| CN110941181B (en) | Rigid-flexible coupling motion platform control method for piezoelectric ceramic connection | |
| Jiao et al. | Active load sensitive electro-hydrostatic actuator on more electric aircraft: Concept, design, and control | |
| CN100368691C (en) | Dynamical pressure feedback electro-hydraulic servo valve | |
| CN204226322U (en) | A kind of electrohydraulic control | |
| CN2851675Y (en) | Electro-hydraulic servo valve for load pressure feedback | |
| Liu et al. | Angle and force hybrid control method for electrohydraulic leveling system with independent metering | |
| JP6393305B2 (en) | Servo actuator | |
| CN216554689U (en) | Electro-hydraulic proportional servo driver and multi-way reversing valve | |
| CN112128153B (en) | Novel variable-pressure-difference load sensing system of constant delivery pump and control method thereof | |
| US2972999A (en) | Two-stage, differential, hydraulic servo valve | |
| CN1752465A (en) | Digital input type electrohydraulic servo-valve | |
| Lantto et al. | Static and dynamic performance of mobile load-sensing systems with two different types of pressure-compensated valves | |
| JP2018025233A (en) | Fluid servo valve, and fluid servo device | |
| CN2412117Y (en) | High-precision synchronous coordination valve | |
| Pratumsuwan et al. | A two-layered fuzzy logic controller for proportional hydraulic system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| PC01 | Cancellation of the registration of the contract for pledge of patent right |
Date of cancellation: 20110823 Granted publication date: 20061213 Pledgee: Industrial Commercial Bank of China Ltd Xiangfan branch Pledgor: Chen Zhenhan Registration number: 2009420000535 |
|
| CX01 | Expiry of patent term |
Expiration termination date: 20150722 Granted publication date: 20061213 |
|
| EXPY | Termination of patent right or utility model |