CN86207117U - Hydraulic pressure vibration servo oil tank - Google Patents
Hydraulic pressure vibration servo oil tank Download PDFInfo
- Publication number
- CN86207117U CN86207117U CN 86207117 CN86207117U CN86207117U CN 86207117 U CN86207117 U CN 86207117U CN 86207117 CN86207117 CN 86207117 CN 86207117 U CN86207117 U CN 86207117U CN 86207117 U CN86207117 U CN 86207117U
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- CN
- China
- Prior art keywords
- mouthful
- chamber
- piston
- mouth
- valve
- 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.)
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- Actuator (AREA)
Abstract
The utility model relates to a hydraulic pressure vibration servo oil tank; the present rectilinear motion servo cylinder is only an actuator element for outputting power and switching energy, and the unlimited periodic motion can not be automatically completed as a hydraulic motor; according to the working principle of the hydraulic motor, the utility model uses the buffering pressure as a reversing pulse signal, uses a hydraulic pressure pulse triggering inverter as a control element, and uses a change valve as a phase retainer-servo cylinder; the automatic reversing control process of the rectilinear motion servo cylinder is realized. The cushion chamber of the utility model can be made into the moveable type, and the scope of application is further expanded.
Description
Present oil cylinder needs the selector valve control could to-and-fro motion as just dynamical element, carries out unlimited periodic motion automatically unlike oil hydraulic motor.Working principle according to oil hydraulic motor, the utility model adopts: hydraulic pulsation is triggered phase inverter (hereinafter to be referred as phase inverter), hydraulicdirectional control valve (hereinafter to be referred as selector valve), hydraulic servo oil cylinder (hereinafter to be referred as oil cylinder) couples together with pipeline, has formed hydraulic vibration servo-cylinder (hereinafter to be referred as oscillator).
The purpose of this utility model provide a kind of with hydraulic oil as working medium, be the automatic reciprocating straight-line Hydraulic power units of major character with the ouput force.
Another purpose of the present utility model is by realizing regulating amplitude with dual-piston structure, adopt variable capacity oil pump as the power input element, just can constituting all adjustable hydraulic oscillator of a frequency of okperation and amplitude.
Description of drawings and enforcement of the present utility model:
Fig. 1 has described composition and the Placement and the working principle of oscillator.
Foot is the selector valve part among the figure, selects existing standard component for use.The left lateral of guiding valve F or right lateral motion are with the high pressure oil " P of working connection
f" switch to " D " mouth or " D ' " mouthful output, promote main piston left lateral or right lateral.The motion of guiding valve F itself is decided by the control pressure size in " B " chamber and " B ' " chamber.
The intermediate portion of Fig. 1 is a phase inverter, and high pressure oil by " R " mouth or " R ' " mouthful output, is connected to " B " chamber and " B ' " chamber, the switching of control selector valve through " P " mouthful input by the road.Phase inverter itself is by a ball valve Q
1With two cone valve Z
1And Z
3Form, its motion is by buffer cavity pressure " P
k" promote.
Fig. 1 the topmost part is an oscillator, by piston rod S and separated type piston h
1And h
2Form, under the effect of " C " chamber or " C ' " chamber high pressure oil, reciprocating motion of the pistons, the function of realization output power.
Fig. 2 is the fundamental diagram that expression oscillator amplitude is regulated.
When needs change the oscillator amplitude, can import high voltage control oil P by the passage from piston rod
L, at P
LEffect under, main piston is divided into two pistons.Piston h wherein
1Be fixed together piston h with piston rod
2Can on piston rod, move horizontally, as shown in Figure 2.As piston h
2Produced displacement distance L
LAfter, the amplitude of piston can be expressed as by formula:
L′＝L－（L
k＋L
k＋2L
h＋L
L）
When controlling oily P
LAfter shutting, utilize the incompressible characteristic of liquid, make the equivalent piston thickening, played the effect of mobile buffer cavity, reached the purpose of regulating hydraulic vibration servo-cylinder amplitude.
Working principle:
Three groups of moving elements of oscillator shown in Figure 1 are equidirectional motions.That is: arrive breeze way when piston motion, produced anti-phase control signal " P
k" or " P
k" after, earlier by the phase inverter assembly (by steel ball Q
1With plunger valve Z
1And Z
2Form) move to the left or to the right and switch delivery pressure " R " and " R ' "; After " R " and " R ' " changed, " B " chamber that is connected by pipeline with them and the pilot pressure in " B ' " chamber also changed, and promote guiding valve F and move; Last because sliding valve movement makes working connection " D " and " D ' " mouthful operating pressure alternate occur, " C " chamber that is attached thereto and " C ' " chamber also change, and promote the motion to the left or to the right of main piston.
As shown in Figure 2, the external connecting pipeline of oil cylinder no longer is two common " G
1" and " G
2", but be provided with " G in addition
3" and " G
4" mouthful, so that buffering pressure is exported as the pulse triggering signal of commutation.
Be example now, specify working procedure with Fig. 1.
Figure 1 shows that the piston right lateral has entered the buffering operating mode, buffer cavity " K " chamber has formed compensator or trimmer pressure P because of being sealed way to cycle oil by the buffer head of piston in " K " chamber
kBecause " K " chamber is by G
3Mouth is communicated with " A " chamber of phase inverter, and its another path is by unidirectional ball valve Q
2Shut, thus " A " cavity pressure increase, to plunger type cone valve Z
1Produce a thrust left, promote plunger type cone valve Z
1, ball valve Q
1With plunger type cone valve Z
2To left movement, as shown in Figure 1.At this moment, ball valve Q
1Mouth is communicated with " P " mouthful partition and with return opening with " R ' ", simultaneously cone valve Z
1" R " mouth is cut off with return opening and be communicated with " P " mouth.The pilot pressure in " B ' " chamber that mouth is connected with " R ' " becomes low pressure by high pressure.In contrast, the pilot pressure in " B " chamber that is communicated with " R " mouth is then uprised by low, promotes selector valve F to left movement (F of guiding valve just shown in Figure 1 is about to begin left lateral state constantly).
The result of selector valve F left lateral motion makes " D " mouth and high pressure come oil " P
f" mouthful connection, the hydraulic oil in " C " chamber of Lian Tonging becomes high pressure by low pressure with it, promotes the piston left lateral; Meanwhile, " D ' " mouth is communicated with return opening, and the high pressure oil pressure in " C ' " chamber of Lian Tonging descends immediately with it, and under the promotion of piston, mouth flows back to fuel tank through " D ' ".
Main piston h
1And h
2And in the operating mode of piston rod S by operation to the right, a series of variations through each above-mentioned cavity pressure will enter into the left lateral operating mode.Can produce pumping action, still " G to " K " chamber during the piston left lateral
1" mouthful with " D " mouth between high pressure oil in the connecting pipeline will push non-return valve Q open
2" A " chamber is replenished, to guarantee carrying out smoothly of commutation process.
As piston h
1And h
2When left lateral arrived the other end, above-mentioned control procedure meeting (is postive direction with the right lateral) repeated, and has so just realized auto reversive purpose.
For by plunger type cone valve Z
1And Z
2And ball valve Q
1The phase inverter of forming has guaranteed bistable characteristic by structure.This be since piston broken away from the commutation operating mode, entered normal operating conditions after, act on Z
1And Q
1On left force rate act on Z
2And Z
1On to the right power big, so, have only by the time piston to enter the buffering operating mode once more and form than working pressure P in " K ' " chamber
fBig compensator or trimmer pressure " P
k' " after, it is anti-phase to trigger phase inverter, and as ball valve Q
1Moved behind the neutral position P
fPressure acts on ball valve Q
1Opposite direction on, make ball valve Q
1Run to terminal point reliably, this characteristics have guaranteed that hydraulic impulse triggers phase inverter and possessed good antijamming capability.
When test work prototype experiment of the present utility model chamber, solenoid directional control valve has been installed on return line, has been attempted the commutation process is disturbed, all failed to influence the normal commutation of hydraulic vibration servo-cylinder.
It is simple in structure to utilize the combination form of plunger type cone valve and ball valve to make, reliable operation.
Claims (2)
1, a kind ofly trigger phase inverter by hydraulic impulse, hydraulicdirectional control valve and hydraulic servo oil cylinder are formed, and the hydraulic vibration servo-cylinder of automatically finishing the straight line periodic motion under the condition of the energy can externally be provided, and it is characterized in that:
A) oil cylinder has four input/output ports: " G
1", " G
2", " G
3", " G
4", " G wherein
1" mouth and " G
2" mouth is positioned at the both sides of hydraulic servo oil cylinder, " G
3" mouth and " G
4" mouthful be to draw by buffer cavity,
B) phase inverter is to be made of plunger type cone valve and ball valve and valve pocket, and two plunger type cone valves are installed in the ball valve both sides respectively,
C) " the G of oil cylinder
1" mouthful be connected " G with " D " of selector valve mouth
2" mouthful be connected with " D ' " of selector valve mouth; " G
3" mouthful be connected " G with " A " chamber of phase inverter
4" mouthful be connected with " A ' " chamber of phase inverter,
D) at " G
1" mouthful connecting pipeline and " G with " D " mouth
3" mouthful with one-way valve " Q being installed between the connecting pipeline in " A " chamber
2", make the hydraulic oil can only be from " G
1" enter " A " chamber in the connecting pipeline mouthful with " D " mouthful,
E) at " G
2" mouthful connecting pipeline and " G with " D ' " mouthful
4" mouthful with one-way valve " Q being housed between the connecting pipeline in " A ' " chamber
3", make the hydraulic oil can only be from " G
2" enter " A ' " chamber in the connecting pipeline mouthful with " D ' " mouthful,
F) two of phase inverter delivery outlets connect with the control chamber of selector valve respectively, wherein " R " mouthful " B " chamber connection together, and " R ' " mouth connects with " B ' " chamber.
2, by the piston in the described oil cylinder of claim 1, it is characterized in that: be by two piston " h
1" and " h
2" composition, wherein piston " h
1" be fixed together piston " h with piston rod
2" can on piston rod, move horizontally, at control oil " P
L" act on down, can equivalence be a thick piston, effective working stroke is shortened, the amplitude of hydraulic oscillator can be regulated in other words.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 86207117 CN86207117U (en) | 1986-09-29 | 1986-09-29 | Hydraulic pressure vibration servo oil tank |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 86207117 CN86207117U (en) | 1986-09-29 | 1986-09-29 | Hydraulic pressure vibration servo oil tank |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN86207117U true CN86207117U (en) | 1988-02-24 |
Family
ID=4809608
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 86207117 Ceased CN86207117U (en) | 1986-09-29 | 1986-09-29 | Hydraulic pressure vibration servo oil tank |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN86207117U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100353080C (en) * | 2002-12-23 | 2007-12-05 | 罗斯控制阀公司 | Electromagnetic valve for reducing energy consumption |
| CN100443743C (en) * | 2007-07-03 | 2008-12-17 | 北京航空航天大学 | Intermittent follower hydraulic cylinder |
| CN101251225B (en) * | 2008-04-09 | 2011-07-20 | 义小毛 | Hydraulic pressure pressure-regulating automatic reverse combined valve for double line grease lubricating system |
| CN101660656B (en) * | 2008-08-29 | 2012-05-02 | 北京中冶华润科技发展有限公司 | Two-point supply valve-type oil feeder |
-
1986
- 1986-09-29 CN CN 86207117 patent/CN86207117U/en not_active Ceased
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100353080C (en) * | 2002-12-23 | 2007-12-05 | 罗斯控制阀公司 | Electromagnetic valve for reducing energy consumption |
| CN100443743C (en) * | 2007-07-03 | 2008-12-17 | 北京航空航天大学 | Intermittent follower hydraulic cylinder |
| CN101251225B (en) * | 2008-04-09 | 2011-07-20 | 义小毛 | Hydraulic pressure pressure-regulating automatic reverse combined valve for double line grease lubricating system |
| CN101660656B (en) * | 2008-08-29 | 2012-05-02 | 北京中冶华润科技发展有限公司 | Two-point supply valve-type oil feeder |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CE01 | Termination of patent right |