CN2082782U - Hydraulic oil return throttling speed gonverning loop equipped with pressure reducing valve interrelated to load - Google Patents
Hydraulic oil return throttling speed gonverning loop equipped with pressure reducing valve interrelated to load Download PDFInfo
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- CN2082782U CN2082782U CN 89221926 CN89221926U CN2082782U CN 2082782 U CN2082782 U CN 2082782U CN 89221926 CN89221926 CN 89221926 CN 89221926 U CN89221926 U CN 89221926U CN 2082782 U CN2082782 U CN 2082782U
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Abstract
The utility model is suitable for the speed regulation of the governor valve of a hydraulic cylinder with a single rod. A pressure reducing valve which is interrelated to load is arranged on the inlet oil line of an oil return throttling speed governing loop, the range of the pressure change of the working cavity of the hydraulic cylinder can be reduced, and the new speed governing loop can be obtained. According to the test result, the combination property of the utility model outperforms the combination property of the existing oil return throttling loop and an oil inlet throttling loop, various processing need can be satisfied. The utility model provides the respective working principle of a directly operated type pressure reducing valve which interrelated to load and a pilot-operated type pressure reducing valve which is interrelated to load, the reasonable range of the ratio of the working area of the remote-control cavity and the direct-control cavity of the directly operated type pressure reducing valve which interrelated to load, the reasonable range of the ratio of the working area of the remote-control cavity and the direct-control cavity of the pilot-operated type pressure reducing valve which is interrelated to load, the structure of a valve port with the good performance and the normalworking condition of the utility model.
Description
The utility model relates to the improvement of hydraulic oil-returning throttle circuit combination property, is applicable to the speed governing of single pole oil hydraulic cylinder series flow control valve.
The prior art of single pole oil hydraulic cylinder series flow control valve speed governing mainly contains meter in and meter out flow control circuit.Active chamber is made with the oil hydraulic cylinder rodless cavity in the entrance throttle governing circuit loop, and rod chamber is made damping cavity, and the meter out flow control circuit is then opposite.Both compare, and the characteristics of meter out flow control circuit are that the damping cavity work area is big.Under dynamic parameters matched well condition, oil hydraulic cylinder can obtain bigger damping force, thereby dynamic characteristic is good.Mainly show as: be difficult for during low speed creeping, have when cutting not have low-frequency vibration, the velocity resonance peak value is little.Its shortcoming is that the active chamber work area is little, and the speed fluctuation amplitude that the restriction obstruction causes is big; The active chamber pressure range is big, thereby the quiet poor rigidity of speed, negative when cutting anticlimax the moving element preshoot serious, empty cut a worker when advancing after the cavity pressure height, frictional loss is big, and is tighter etc. to the oil circuit seal request.The pluses and minuses in meter in loop are just in time opposite with the meter out loop.In addition, meter out loop pumping hole links to each other with the oil hydraulic cylinder damping cavity, and operating rate is directly disturbed in the pressure pulsation of pump.The series flow control valve in meter in loop has filter action, can reduce above-mentioned interference.But the pressure skew of back pressure valve can cause velocity jump.
A kind of prior art of improving the combination property of single pole oil hydraulic cylinder series flow control valve speed governing is to adopt to become back pressure entrance throttle governing circuit loop.This technology is in all reflections to some extent of " modular machine tool and automation processing technique " the 2nd phase in 1988, " lathe and hydraulic pressure " the 2nd phase in 1987 and 1984 the 1st phases.The relevant back pressure valve of its applied load replaces common back pressure valve.The valve core movement of the relevant back pressure valve of load.Controlled jointly by oil hydraulic cylinder two cavity pressures, back pressure raise automatically when load was reduced.Compare with the meter in loop of deciding back pressure, this loop works cavity pressure excursion is less, thereby has improved the quiet rigidity of speed, the preshoot when having reduced the load anticlimax.But it makes the dynamic parameters on oil hydraulic cylinder two cavity oil road produce cross, thereby has reduced the damping force of moving element, has reduced the stable deposit of dynamical system, make meter in loop damping deficiency defective more serious.
Task of the present utility model provides a kind of good combination property, can satisfy the novel meter out flow control circuit of multiple processing needs.
Technical conceive of the present utility model is as follows: a series of shortcomings of meter out flow control circuit are the excessive generations of hydraulic cylinder works cavity pressure excursion.If the relevant reduction valve of load is set on its in-line, control the action of this valve by the pressure signal of in-line and oil circuit, damping cavity pressure is reduced with load and reduce, just can reduce the active chamber pressure amplitude, thereby it is big to obtain a kind of reservation meter out loop damping power, advantages such as dynamic characteristic is good, and can overcome its static velocity poor rigidity, load preshoot is big, empty during anticlimax the new loop of shortcomings such as active chamber overpressure when cutting.The relevant reduction valve of load also can reduce the interference of pumping hole pressure pulsation to operating rate.
Fig. 1 is a hydraulic schematic diagram of the present utility model.(it can use the constant pressure type variable displacement pump to the utility model by oil sources (1), limit pressure type variable pump or metering pump add relief valve, among the figure only expression use limit pressure type variable pump), compositions such as single pole oil hydraulic cylinder (2), series flow control valve (3), the relevant reduction valve (4) of load and auxiliary element.Feature of the present utility model is to be provided with the relevant reduction valve (4) of load at oil sources (1) to the oil circuit of single pole oil hydraulic cylinder (2).
Key of the present utility model partly is the relevant reduction valve (4) of load, and it can be divided into two kinds of direct-acting type and leading types.The following describes their working principle.
Fig. 2, Fig. 3 are respectively the structural representations of direct-acting type and the relevant reduction valve of leading type load.They have four outer oil-collecting holes: import P
1Should connect oil sources, outlet P
2Should connect the oil hydraulic cylinder rodless cavity, remote control mouth K should connect oil hydraulic cylinder rod chamber oil circuit, and leakage hole L answers connected tank.Liquid stream is from import P
1In the inflow valve, through pressure-reduction outlet decompression back from exporting P
2Flow out.The principle that these two kinds of valves all utilize the hydraulic coupling that acts on the spool (5) and spring force to balance each other, maintaining valve outlet P
2Be approximately a negative constant with the ratio of the steady state pressure variable quantity of remote control mouth K.In the loop of Fig. 1, when load reduced, oil hydraulic cylinder rodless cavity pressure reduced and the rising of rod chamber pressure.The pressure-reduction outlet of the relevant reduction valve of load this moment turns down automatically, to guarantee that the value added that reduces to be worth with rod chamber pressure of rodless cavity pressure is approximated to ratio under new state of equilibrium.
The condition of the loop proper functioning of Fig. 1 is: when load was maximum, the pressure of oil hydraulic cylinder rod chamber was not less than 4～5bar, and the pressure drop of the relevant reduction valve of load is not less than 2～3bar.Above-mentioned pressure should not transferred too much yet, in order to avoid reduce circuit efficiency.
The following describes the structure characteristic of leading type and the relevant reduction valve of direct-acting type load.
The no spring terminal of the main valve of leading type valve and direct-acting type valve all has straight control chamber (6) and remote control chamber (7) of mutual separation.The outlet P of straight control chamber (6) and valve
2Communicate, remote control chamber (7) communicate with the remote control mouth K of valve, as Fig. 3 and shown in Figure 2.The dynamic and static characteristic in the comparison loop of the work area in remote control chamber (7) and straight control chamber (6) has material impact.This ratio is more little, and then the dynamic characteristic in loop is good more and static characteristic is more bad.The reasonable value of this ratio is 0.40 to 1.12.
The valve port structure of the main valve of direct-acting type valve and leading type valve also has material impact to the sound characteristic in loop.When valve port adopted axial triangle slot type structure, the loop had good dynamic response when middle low speed.Fig. 4 represents a kind of structure that the spool (5) of axial triangle slot type valve port is arranged.Fig. 5 is the sectional view along the A-A line.It is characterized in that the passage section that is shaped on more than two or two at the valve port place of spool (5) is a leg-of-mutton axial triangular groove (8).Only represent to have the valve port structure of four axial triangular grooves among the figure.
Provide an example below, and the explanation implementation result.
Embodiment is a modular machine tool hydraulic pressure moving platform, can realize that F.F.-worker advances-rewind down-stop semi-automatic work circulation, its hydraulic schematic diagram as shown in Figure 6, the electromagnet action schedule sees the following form:
The electromagnet action schedule
| IDT | 2DT | 3DT | |
| F.F. | ＋ | － | ＋ |
| The worker advances | － | ＋ | ＋ |
| Rewind down | ＋ | － | － |
| Stop | － | － | － |
Compare with existing meter out flow control circuit, set up the relevant reduction valve (4) of load on the in-line of present embodiment when the worker advances.The relevant reduction valve (4) of load is a directly controlled type.Its remote control chamber is 0.5～1.0 with the ratio of straight control chamber work area, and the amplitude of variation that can guarantee the hydraulic cylinder works cavity pressure is less than the meter in loop, and this valve valve port structure is axial triangle slot type.
Comparative test result shows, no matter unloaded, have and carry and low speed, middling speed, high speed worker advance etc. under the operating mode, the low frequency component of speed one time graph of the present utility model is ideal line, obviously is better than existing oil-feed and meter out flow control circuit.The preshoot that static velocity rigidity, load dump, F.F. are changed a job when into advancing crawl with the worker all is better than the meter out flow control circuit significantly, is not inferior to the entrance throttle governing circuit loop.In addition, the utility model also can bear negative cutting force, thereby has good comprehensive performances, can satisfy multiple processing needs, and its implementation cost is a little more than the meter out loop, and identical with the meter in loop.
Claims (7)
1, a kind of hydraulic oil-returning throttling speed control circuit of being made up of oil sources [1], single pole oil hydraulic cylinder [2], series flow control valve [3] and auxiliary element etc. is characterized in that oil sources [1] is provided with direct-acting type or the relevant reduction valve [4] of leading type load to the oil circuit of single pole oil hydraulic cylinder [2].
2, a kind of by the said loop of claim 1, the no spring terminal that it is characterized in that the relevant reduction valve of direct-acting type load on this loop has straight control chamber (6) and remote control chamber (7) of mutual separation, wherein directly controls the outlet P of chamber (6) and this valve
2Communicate, remote control chamber (7) communicate with remote control mouth k.
3, a kind of claim 1 and 2 described loops of pressing is characterized in that the work area in the remote control chamber (7) of the relevant reduction valve of direct-acting type load on the loop is 0.40 to 1.12 with the straight ratio of controlling the work area in chamber (6).
4, a kind of by claim 2 and 3 described loops, it is characterized in that the relevant reduction valve of direct-acting type load on the loop has the passage section more than two or two at the valve port place of spool (5) be leg-of-mutton axial triangular groove (8).
5, a kind of by the said loop of claim 1, the no spring terminal that it is characterized in that the relevant reduction valve main valve of leading type load on this loop has straight control chamber (6) and remote control chamber (7) of mutual separation, wherein directly controls the outlet P of chamber (6) and this valve
2Communicate, remote control chamber (7) communicate with the remote control mouth k of this valve.
6, a kind of described loop of claim 5 of pressing is characterized in that the work area in the relevant reduction valve main valve remote control chamber (7) of leading type load on the loop is 0.40 to 1.12 with the straight ratio of controlling the work area in chamber (6).
7, a kind of by claim 5 and 6 described loops, the valve port that it is characterized in that the relevant reduction valve valve core of main valve (5) of leading type load on the loop is in through-flow more than two or two, and the cross section is a leg-of-mutton axial triangular groove (8).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 89221926 CN2082782U (en) | 1989-12-31 | 1989-12-31 | Hydraulic oil return throttling speed gonverning loop equipped with pressure reducing valve interrelated to load |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 89221926 CN2082782U (en) | 1989-12-31 | 1989-12-31 | Hydraulic oil return throttling speed gonverning loop equipped with pressure reducing valve interrelated to load |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2082782U true CN2082782U (en) | 1991-08-14 |
Family
ID=4876292
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 89221926 Granted CN2082782U (en) | 1989-12-31 | 1989-12-31 | Hydraulic oil return throttling speed gonverning loop equipped with pressure reducing valve interrelated to load |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2082782U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105637233A (en) * | 2013-10-11 | 2016-06-01 | Ｋｙｂ株式会社 | Control system for hybrid construction machine |
| CN112393895A (en) * | 2019-08-14 | 2021-02-23 | 宝山钢铁股份有限公司 | Cold rolling mill fine cooling injection valve dynamic and static characteristic parameter testing device and testing method |
-
1989
- 1989-12-31 CN CN 89221926 patent/CN2082782U/en active Granted
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105637233A (en) * | 2013-10-11 | 2016-06-01 | Ｋｙｂ株式会社 | Control system for hybrid construction machine |
| CN112393895A (en) * | 2019-08-14 | 2021-02-23 | 宝山钢铁股份有限公司 | Cold rolling mill fine cooling injection valve dynamic and static characteristic parameter testing device and testing method |
| CN112393895B (en) * | 2019-08-14 | 2022-07-15 | 宝山钢铁股份有限公司 | Cold rolling mill fine cooling injection valve dynamic and static characteristic parameter testing device and testing method |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |