CN207920989U - A kind of throttling speed control circuit for maintaining hydraulic pressure system speed to stablize - Google Patents
A kind of throttling speed control circuit for maintaining hydraulic pressure system speed to stablize Download PDFInfo
- Publication number
- CN207920989U CN207920989U CN201820351384.5U CN201820351384U CN207920989U CN 207920989 U CN207920989 U CN 207920989U CN 201820351384 U CN201820351384 U CN 201820351384U CN 207920989 U CN207920989 U CN 207920989U
- Authority
- CN
- China
- Prior art keywords
- valve
- pressure
- cylinder
- hydraulic
- throttle 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.)
- Expired - Fee Related
Links
Landscapes
- Fluid-Pressure Circuits (AREA)
Abstract
The utility model discloses a kind of throttling speed control circuits that maintenance hydraulic pressure system speed is stablized, including hydraulic cylinder（1）, throttle valve（2）, quantitative hydraulic pump（3）And overflow valve（4）, overflow valve（4）And hydraulic cylinder（1）It is parallel to quantitative hydraulic pump（3）Flowexit, hydraulic cylinder（1）Pass through throttle valve（2）It is connected to quantitative hydraulic pump（3）, the overflow valve（4）For pilot operated compound relief valve；It further include the constant cylinder of pressure difference（6）, pressure switch（5）And solenoid directional control valve（7）, the constant cylinder of pressure difference（6）One end pass through pressure switch（5）With throttle valve（2）Outlet be connected, the other end passes through solenoid directional control valve（7）With overflow valve（4）Remote control orifice be connected.The utility model accesses two-position two-way electromagnetic directional valve and pilot operated compound relief valve in the constant cylinder of the outlet of throttle valve access pressure difference and pressure switch, in the import of throttle valve by the constant cylinder of pressure difference, and hydraulic pressure system speed can effectively be maintained to stablize.
Description
Technical field
The utility model is related to the stability control fields of hydraulic system speed, more particularly to a kind of maintenance hydraulic system
Speed stable throttling speed control circuit.
Background technology
Hydraulic system is often run in the case of low-speed heave-load, if the speed of system becomes during the work time
Change, just certainly exists acceleration, the equilibrium state of system is broken, and system just will appear vibration and noise, is influencing system just
Often work.According to fluid mechanics knowledge：Speed of service v=q/A of hydraulic system, v- speed in formula, q- enter hydraulic cylinder
Fluid flow, the piston effective area of A- hydraulic cylinders.It, can be with from formula because the piston effective area A of hydraulic cylinder is fixed
Find out：Into the fluid flow q variations of hydraulic cylinder, necessarily cause the speed of service v variations of hydraulic system, that is to say, that hydraulic pressure
The speed v of system is fluctuated with flow q fluctuations.As long as flow q stablizes, speed v centainly stablizes.
From the point of view of Hydraulic Industry, the basic principle of speed governing is all to realize speed governing by changing the flow of fluid, speed governing
It is required that be flow stability it is better, the balance of system is better.
From technological layer, by adjusting flow, come the circuit of speed governing, there are two types of types：
1, with the speed control loop of conventional throttle valve
With the speed control loop of conventional throttle valve（Such as Fig. 1）Principle be：Using quantitative oil pump feed, quantitative pump discharge parallel connection one
A overflow valve, the pressure pumped in circuit are held essentially constant after being set up by overflow valve.The flow of output is pumped, a part enters hydraulic pressure
Cylinder pushes piston motion, another part flow to flow back to fuel tank through overflow valve.Flow can be realized by adjusting the circulation area of throttle valve
It adjusts, to realize the speed governing of hydraulic cylinder.
But according to hydrodynamics：Pass through flow q=KA (Δ P) of throttle valve1/2（It is also the stream into hydraulic cylinder
Amount）.Q- passes through the flow of throttle valve, the flow area of A- throttle valves, the inlet outlet pressure differential of Δ P- throttle valves, K- constants in formula.
When one timing of throttle valve opening, when the load F of cylinder increases, Δ P necessarily reduces, then the flow q into hydraulic cylinder also necessarily subtracts
It is small, therefore the speed of service of hydraulic cylinder also necessarily reduces.Conversely, as the same.So the maximum drawback in this circuit is exactly：Hydraulic pressure
The movement velocity of cylinder is fluctuated with the fluctuation of load F.
2, with the speed control loop of speed governing valve
Speed governing valve be throttle valve with reducer unit at combination valve, speed governing valve at work, acts on throttle valve valve port two
The pressure difference at end can keep being basically unchanged, then being also maintained for being basically unchanged by the flow of speed governing valve.Therefore, with speed governing valve
The hydraulic system speed of speed control loop is also basicly stable, and balance is preferable.
But still there are these disadvantages with the speed control loop of speed governing valve：1. due to the starting stage of system work, decompression
Valve is opened completely, therefore the flow of system is only controlled by throttle valve, and system at this time is exactly a speed governing with conventional throttle valve
Circuit, the speed of system are still to be fluctuated with the fluctuation of load, and stability is still poor；2. since speed governing valve is by pressure reducing valve and section
Stream valve be composed, the dependence spring of pressure reducing valve itself does not solve come the defect balanced, restriction both ends pressure difference always
It is unable to precise constant, illustrates that system fluctuation still has.3. speed governing valve is complicated, the accuracy of manufacture is high, of high cost.
Utility model content
The purpose of the utility model is to overcome the deficiencies in the prior art, provide what a kind of maintenance hydraulic pressure system speed was stablized
Throttling speed control circuit.
The purpose of this utility model is achieved through the following technical solutions：It is a kind of that hydraulic pressure system speed is maintained to stablize
Throttling speed control circuit, including hydraulic cylinder, throttle valve, quantitative hydraulic pump and overflow valve, the overflow valve and hydraulic cylinder are parallel to
The flowexit of the quantitative hydraulic pump, the hydraulic cylinder are connected to quantitative hydraulic pump by throttle valve, and the overflow valve is first
Conduction overflow valve；
Further include the constant cylinder of pressure difference, one end of the constant cylinder of pressure difference is connected with the outlet of the throttle valve, the other end with
The remote control orifice of the overflow valve is connected；
Further include pressure switch and solenoid directional control valve, one end of the constant cylinder of pressure difference by pressure switch with it is described
The outlet of throttle valve is connected, and the other end is connected by solenoid directional control valve with the remote control orifice of the overflow valve.
The solenoid directional control valve is two-position two-way electromagnetic directional valve.
The utility model has the beneficial effects that：
1）The constant cylinder of pressure difference and throttle valve are used in parallel, and throttling valve outlet is connected with one end of the constant cylinder of pressure difference, throttle valve
Import is connected with the other end of the constant cylinder of pressure difference, and how the not load of guard system is fluctuated, and the pressure difference of throttle valve import is constant, hydraulic pressure
The movement velocity all-the-time stable of system, to solve the problems, such as that hydraulic system speed is fluctuated with the fluctuation of load.
2）It is connected with one end of the constant cylinder of pressure difference with the remote control orifice of pilot operated compound relief valve, has both solved throttle valve import
The followability that pressure is fluctuated with system load, and solve the pressure limiting flooding problems of system.
3）It is used in combination with pressure switch and two-position two-way electromagnetic directional valve, to solve cutting for pump intake pressure control mode
It changes.
Description of the drawings
Fig. 1 is the structural schematic diagram of throttling speed control circuit in the prior art；
Fig. 2 is the structural schematic diagram of the utility model；
In figure, 1- hydraulic cylinders, 2- throttle valves, 3- quantitative hydraulic pumps, 4- overflow valves, 5- pressure switches, 6- pressure differences are constant
Cylinder, 7- solenoid directional control valves.
Specific implementation mode
Below in conjunction with embodiment, the technical solution of the utility model is clearly and completely described, it is clear that retouched
The embodiment stated is only the utility model a part of the embodiment, instead of all the embodiments.Based in the utility model
Embodiment, the every other embodiment that those skilled in the art are obtained under the premise of not making the creative labor, all belongs to
In the range of the utility model protection.
Referring to Fig.2, the utility model provides a kind of technical solution：A kind of throttle grverning for maintaining hydraulic pressure system speed to stablize
Circuit, including hydraulic cylinder 1, throttle valve 2, quantitative hydraulic pump 3 and overflow valve 4, the overflow valve 4 and hydraulic cylinder 1 are parallel to institute
The flowexit of quantitative hydraulic pump 3 is stated, the hydraulic cylinder 1 is connected to quantitative hydraulic pump 3 by throttle valve 2.
The throttling speed control circuit refers specifically to entrance throttle governing circuit circuit, and throttle valve 2 is installed in series in quantitative hydraulic pump 3
Outlet and the entrance of hydraulic cylinder 1 between, so referred to as entrance throttle governing circuit circuit.The fluid that the quantitative hydraulic pump 3 exports
A part by throttle valve 2 flow into hydraulic cylinder 1 rodless cavity push piston motion, another part fluid by with quantitative hydraulic pump
3 overflow valves 4 in parallel flow back to hydraulic oil container.Since overflow valve 4 has overflow, the outlet pressure of quantitative hydraulic pump 3 is exactly overflow valve 4
Adjustment pressure, and this value is held essentially constant.Adjust the opening area of throttle valve 2, you can change the stream by throttle valve 2
Amount, to adjust the movement velocity of 1 piston of hydraulic cylinder.
The overflow valve 4 is pilot operated compound relief valve, because the pressure on main valve plug top is by the pressure of pilot valve and damping hole
Drop determines, when operating pressure is very big, but the also hour of the pressure drop on pilot valve and damping hole, then acting on main valve plug
Pressure difference is also small, in this way, operating pressure is big again, the condition that overflow occurs is also only related with pressure difference, also, this pressure difference is only more than master
Overflow could occur after the counter-forces such as spool gravity, frictional force, therefore, pilot operated compound relief valve 4 overcomes direct-acting overflow valve can only
The problem of work at low pressures, more practicability.
The throttling speed control circuit that a kind of maintenance hydraulic pressure system speed is stablized further includes the constant cylinder 6 of pressure difference, the pressure
One end of poor constant cylinder 6 is connected with the outlet of the throttle valve 2, and the other end is connected with the remote control orifice of the overflow valve 4.
Since overflow valve 4 and 2 parallel connection of throttle valve have obtained overflow throttle valve, then a high pressure oil part for entrance is through throttling
Valve 2 goes to executing agency, and overflow port of the another part through overflow valve 4 removes fuel tank, 4 upper and lower end of overflow valve respectively with before and after throttle valve 2
Pressure oil communicate, when outlet pressure increases, spool moves down, and turns down overflow port, and spillage drag increases, and inlet pressure increases therewith
Add, thus the pressure difference before and after throttle valve 2 is held essentially constant constant, i.e. the pressure difference at constant 6 both ends of cylinder of pressure difference is constant all the time not
Become, vice versa.
Specifically, the throttling speed control circuit that a kind of maintenance hydraulic pressure system speed is stablized further includes pressure switch 5
It is connected with the outlet of the throttle valve 2 by pressure switch 5 with one end of solenoid directional control valve 7, the constant cylinder of the pressure difference 6, separately
One end is connected by solenoid directional control valve 7 with the remote control orifice of the overflow valve 4.
The pressure switch 5 be in hydraulic system when Fluid pressure reaches predetermined value, make electric contact act element.
When system pressure reaches the setting of pressure switch 5, electric signal is sent out, electrical equipment is made（Such as electromagnet, motor, time
Relay, electromagnetic clutch etc.）Action makes oil circuit release, commutation, executive component realize sequentially-operating, or close motor to make
System stalls play safeguard protection etc..
There is closed chamber in the solenoid directional control valve 7, is provided with through-hole in different location, each hole connects different oil
It manages, is piston among chamber, two sides is two blocks of electromagnet, which side the magnet coil energization valve body in which face will be attracted to, and pass through
The movement of application valve body is turned on and off different outages, and fuel feed hole is normally opened, and hydraulic oil will enter different
Then oil exit pipe pushes the piston of oil cylinder, piston that piston rod, piston rod is driven to drive mechanical device again by the pressure of oil,
In this way mechanical movement is just controlled by controlling the current switching of electromagnet.
Preferably, the solenoid directional control valve 7 is two-position two-way electromagnetic directional valve, specifically, the bi-bit bi-pass electromagnetism
Reversal valve is step direct-acting type electromagnetic valve, it is a kind of direct acting and the principle that pilot-operated type is combined, when entrance and outlet are not pressed
When poor, after energization, electromagnetic force directly upwards in turn lifts the small valve of guide and main valve closure member, valve open, when entrance with go out
When mouthful reaching switch DP, after energization, the small valve of electromagnetic force guide, cavity pressure rises under main valve, and upper cavity pressure declines, to utilize
Pressure difference is upwards pushed main valve open；When power-off, pilot valve pushes closure member using spring force or pressure medium, moves down, makes valve
Door is closed.
When system is just started to work, system pressure zero, pressure switch 5 is failure to actuate, at two-position two-way electromagnetic directional valve 7
In cut-off state, pilot operated compound relief valve 4 is closed, and the output fluid of quantitative hydraulic pump 3 fully enters system, system is made quickly to be formed
Initial pressure.
System initial pressure once being formed, just start to work by pressure switch 5, and two-position two-way electromagnetic directional valve 7 is switched to
Unicom state, pump intake pressure are just determined by the remote control orifice of pilot operated compound relief valve 4, at this point, the outlet of throttle valve 2 is permanent with pressure difference
The one end for determining cylinder 6 is connected, and the import of throttle valve 2 is connected with the other end end of the constant cylinder of pressure difference, the inlet outlet pressure differential Δ of throttle valve 2
P=P1-P2=G/A, then Δ P is constant, so flow q=KA (Δ P)1/2It is also constant, the then movement velocity of hydraulic system
It is constant.
If system load increases, the pressure P of constant 6 one end of cylinder of pressure difference1Also increase therewith, according to stress balance equation P1A1+
G=P2A2, the pressure P of constant 6 other end of cylinder of pressure difference2Also corresponding to increase, but due to Δ P=P2-P1The value of=G/A is constant always
, then the movement velocity of hydraulic system is also stable always.
To adjust the inlet outlet pressure differential Δ P of throttle valve 2, then change the weight that the constant cylinder 6 of pressure difference is hung.
The above is only the preferred embodiment of the utility model, it should be understood that the utility model is not limited to herein
Disclosed form is not to be taken as excluding other embodiments, and can be used for other combinations, modifications, and environments, and
Can be in contemplated scope described herein, modifications can be made through the above teachings or related fields of technology or knowledge.And this field
The modifications and changes that personnel are carried out do not depart from the spirit and scope of the utility model, then all rights appended by the utility model
It is required that protection domain in.
Claims (2)
1. a kind of throttling speed control circuit for maintaining hydraulic pressure system speed to stablize, including hydraulic cylinder（1）, throttle valve（2）, quantitative hydraulic
Pump（3）And overflow valve（4）, the overflow valve（4）And hydraulic cylinder（1）It is parallel to the quantitative hydraulic pump（3）Flowexit,
The hydraulic cylinder（1）Pass through throttle valve（2）It is connected to quantitative hydraulic pump（3）, it is characterised in that：The overflow valve（4）For guide
Formula overflow valve；
It further include the constant cylinder of pressure difference（6）, the constant cylinder of pressure difference（6）One end and the throttle valve（2）Outlet be connected, it is another
End and the overflow valve（4）Remote control orifice be connected；
It further include pressure switch（5）And solenoid directional control valve（7）, the constant cylinder of pressure difference（6）One end pass through pressure switch
（5）With the throttle valve（2）Outlet be connected, the other end passes through solenoid directional control valve（7）With the overflow valve（4）Remote control
Mouth is connected.
2. a kind of throttling speed control circuit for maintaining hydraulic pressure system speed to stablize according to claim 1, it is characterised in that：Institute
The solenoid directional control valve stated（7）For two-position two-way electromagnetic directional valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201820351384.5U CN207920989U (en) | 2018-03-15 | 2018-03-15 | A kind of throttling speed control circuit for maintaining hydraulic pressure system speed to stablize |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201820351384.5U CN207920989U (en) | 2018-03-15 | 2018-03-15 | A kind of throttling speed control circuit for maintaining hydraulic pressure system speed to stablize |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN207920989U true CN207920989U (en) | 2018-09-28 |
Family
ID=63598863
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201820351384.5U Expired - Fee Related CN207920989U (en) | 2018-03-15 | 2018-03-15 | A kind of throttling speed control circuit for maintaining hydraulic pressure system speed to stablize |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN207920989U (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109877200A (en) * | 2019-03-04 | 2019-06-14 | 中国电子科技集团公司第四十九研究所 | A kind of stainless steel protection pipe slot rolling forming machine and slot rolling manufacturing process |
| CN110529463A (en) * | 2019-07-24 | 2019-12-03 | 徐州工程学院 | A kind of flexible hydraulic throttling speed control circuit experimental system |
| CN111577682A (en) * | 2020-05-19 | 2020-08-25 | 华侨大学 | Two-way speed regulating valve based on variable pressure difference active control |
| CN111706564A (en) * | 2020-06-03 | 2020-09-25 | 华侨大学 | A Two-Way Speed Control Valve Based on Active Control of Volumetric Differential Pressure |
| CN111706563A (en) * | 2020-06-03 | 2020-09-25 | 华侨大学 | A three-way speed regulating valve based on hydraulic motor-generator pressure compensator |
| CN113700706A (en) * | 2021-07-09 | 2021-11-26 | 武汉船用机械有限责任公司 | Hydraulic control system for lifting device |
-
2018
- 2018-03-15 CN CN201820351384.5U patent/CN207920989U/en not_active Expired - Fee Related
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109877200A (en) * | 2019-03-04 | 2019-06-14 | 中国电子科技集团公司第四十九研究所 | A kind of stainless steel protection pipe slot rolling forming machine and slot rolling manufacturing process |
| CN109877200B (en) * | 2019-03-04 | 2020-07-17 | 中国电子科技集团公司第四十九研究所 | Roll groove forming machine and roll groove forming method for stainless steel protection pipe |
| CN110529463A (en) * | 2019-07-24 | 2019-12-03 | 徐州工程学院 | A kind of flexible hydraulic throttling speed control circuit experimental system |
| CN111577682A (en) * | 2020-05-19 | 2020-08-25 | 华侨大学 | Two-way speed regulating valve based on variable pressure difference active control |
| CN111706564A (en) * | 2020-06-03 | 2020-09-25 | 华侨大学 | A Two-Way Speed Control Valve Based on Active Control of Volumetric Differential Pressure |
| CN111706563A (en) * | 2020-06-03 | 2020-09-25 | 华侨大学 | A three-way speed regulating valve based on hydraulic motor-generator pressure compensator |
| CN111706563B (en) * | 2020-06-03 | 2022-05-03 | 华侨大学 | Three-way speed regulating valve based on hydraulic motor-generator pressure compensator |
| CN113700706A (en) * | 2021-07-09 | 2021-11-26 | 武汉船用机械有限责任公司 | Hydraulic control system for lifting device |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN207920989U (en) | A kind of throttling speed control circuit for maintaining hydraulic pressure system speed to stablize | |
| CN104989690B (en) | Overload relief valve | |
| CN201560422U (en) | An electro-hydraulic proportional control piston type single lifting point hydraulic hoist | |
| CN104132016A (en) | Three-way flow valve, load-sensitive multi-way valve, hydraulic system and engineering machinery | |
| CN206246446U (en) | Integrated hydraulic valve group and the fluid power system and concrete pump of the valve group are set | |
| CN108443257A (en) | A kind of servo variable mechanism of hydraulic pump motor | |
| CN104564862A (en) | Combined pump-controlled cylinder electric hydraulic control system | |
| CN103663296A (en) | Cylindrical-linear-motor-driven electro-hydraulic proportional directional screw-in multi-way cartridge valve for forklifts | |
| CN106194680A (en) | The axial plunger pump installation of a kind of high accuracy electric proportional control and control method | |
| CN108561363A (en) | A kind of side valve type one-way hydraulic balance fastening system | |
| CN101149068A (en) | Electro-hydraulic proportional relief valve | |
| CN108980137A (en) | A kind of executing agency of high response long-life high reliability | |
| CN115681235A (en) | Double-active control high-pressure large-flow high-water-base digital throttle valve and control method | |
| CN205918570U (en) | Axial plunger pump device of high accuracy electric proportional control | |
| CN104179734B (en) | A kind of constant-pressure control device for hydraulic pump and control method | |
| CN208363156U (en) | Valve system drops in a kind of bull-dozer fastly | |
| CN203926197U (en) | A kind of for the anti-hydraulic shock relief valve of load-transducing | |
| CN207961100U (en) | A kind of hydraulic control system of flap valve device | |
| CN204344551U (en) | A kind of dynamic beam governor oil line structure of hydraulic press | |
| CN215171162U (en) | Improved hydraulic system of double-hoisting-point gate hoist | |
| CN212250665U (en) | Electro-hydraulic multi-speed control system for near-water medium | |
| CN202144805U (en) | Electrical modulation proportional throttle control valve | |
| CN104030199A (en) | Forklift hydraulic system with bypass oil way throttling speed regulation loop | |
| CN202194888U (en) | Hydraulic flushing valve | |
| CN107100909B (en) | A kind of intelligent control energy-saving valve |
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: 20180928 Termination date: 20190315 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |