CN105952705B - Balanced valve - Google Patents
Balanced valve Download PDFInfo
- Publication number
- CN105952705B CN105952705B CN201610559900.9A CN201610559900A CN105952705B CN 105952705 B CN105952705 B CN 105952705B CN 201610559900 A CN201610559900 A CN 201610559900A CN 105952705 B CN105952705 B CN 105952705B
- Authority
- CN
- China
- Prior art keywords
- valve
- port
- control
- hydraulic fluid
- balance
- 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.)
- Active
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/18—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on either side
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The present invention relates to a kind of balanced valve, it is characterised in that：Including valve body, the first hydraulic fluid port, the second hydraulic fluid port, control port are provided with valve body；Balance valve pocket；Balance valve core in balance valve pocket, balance valve core inside have ladder hole, and the control chamber balanced in valve pocket is separated into independent ante-chamber and back cavity two parts by balance valve core；Pilot valve in the ladder hole of balance valve core, pilot valve is held by the first spring and keeps reach trend, the front end of pilot valve is located in the small-bore portion of ladder hole, the rear end of pilot valve is located in the heavy caliber portion of ladder hole, the 3rd damping hole is equipped with the rear end of pilot valve, throttling channel is provided with the front end periphery wall of pilot valve；Under pilot valve reach state.It is it is a kind of it is simple and reasonable, can stability contorting balance valve core aperture, from load disturbance, allow it is larger installation moment of torsion balanced valve.
Description
Technical field
The present invention relates to a kind of hydraulic valve, a kind of especially hydraulically balanced valve that load stabilization can be kept to transfer.
Background technology
In the mechanical equipments such as modern engineering machinery, building machinery, raising hydraulic circuit is widely applied, in concrete pump
In the swing arm and receipts arm system of car, commonly used balanced valve carries out hydraulic locking, to ensure that arm support can be reliable at an arbitrary position
Stop.Wherein, balanced valve is the crucial Hydraulic Elements of load control system and hydraulic pressure load bearing system, and the performance of balanced valve is good and bad straight
Connecing influences the running quality of host.And with the increasing of concrete mixer job requirements difficulty, leakproofness, self-locking to balanced valve
The requirement of property, stationarity and multifunctionality is higher and higher, and the power density of balanced valve itself is also increasing.It is high with operation
The continuous refreshing of degree, the operating pressure of pumping vehicle arm rack system are also constantly soaring.In this context, concrete mixer arm how is improved
Frame system safety work performance becomes research focus.
Common a kind of load using balanced valve that Figure 10 is shown in the boom system for concrete mixer controls
Hydraulic system.Its operation principle is：When reversal valve 3 ', which is switched to load, declines working position, the A mouths of reversal valve 3 ' are fuel-displaced, fluid
Into the rod chamber Y of arm support oil cylinder, part fluid enters liquid controling cavity (plunger shaft) Pil of balanced valve through Px mouthfuls and damping hole 1 ',
So as to open balanced valve 2 ', the C mouths of the fluid of rodless cavity W through balanced valve 2 ' with V mouthfuls and the B mouth oil return box T of reversal valve 3, then
Weight G declines；When reversal valve 3, which is switched to load, rises working position, B mouthfuls fuel-displaced, and fluid is (flat through the check valve in balanced valve 2 '
The agent structure of weighing apparatus valve generally comprises the overflow valve and check valve of parallel connection, as shown in Figure 4) enter oil cylinder rodless cavity W, rod chamber Y
A oil return box T of the fluid through reversal valve 3 ', weight G rises.When reversal valve 3 ' does not switch, balanced valve 2 ' is then closed, and seals up C
The fluid of mouth and oil cylinder rodless cavity W, keeps weight G in desired position.There are a variety of insufficient and scarce for hydraulic system in Fig. 4
Fall into.Such as when being transferred to fast operating shelves, the hydraulic oil on working connection can quickly be increased by Px mouthfuls of pressure with flow, flat
Weighing apparatus valve 2 ' can cause compression shock when opening to the conventional pilot control valve portion of balanced valve, this impact may cause balanced valve to be dashed forward
So open, so as to cause equipment job insecurity.In addition the control pressure narrow range of the balanced valve in Fig. 4, pressure and flow waves
Dynamic big, balanced valve opening process micro-control and stability are poor.This control pressure fluctuation of balanced valve can be led with control flowed fluctuation
The aperture of balanced valve 2 ' is caused to produce change so that the piston position in arm support oil cylinder is difficult to be maintained on exact position.Therefore, pacify
Balanced valve in very long arm support oil cylinder be easily in the presence of it is a kind of unstable, cause equipment uncontrollability and
Make equipment be operated in it is dangerous in the state of.
As Authorization Notice No. CN103104565B entitled " balanced valve " patent of invention in disclose a kind of balanced valve.But
There are a variety of deficiencies and defect for this balanced valve.
1st, the pilot valve of balanced valve is a steel ball in the invention, it is necessary to very accurate in the small opening control of balanced valve
Pilot pressure control could realize the slowly varying unexpected opening impact to avoid balanced valve of flow.This is in general hydraulic pressure system
It is difficult to carry out in system.
2nd, the unlatching of balanced valve main valve plug be by load pressure, what control pressure together decided on, therefore the change of load pressure
Change can cause main valve plug opening to change, and then cause changes in flow rate, cause host to shake.
3rd, pilot control level only has the pressure reducing circuit of 2 damping compositions, big since load change produces in X mouthfuls of control pressures
Fluctuation when, it is impossible to play cushioning effect well, can cause balanced valve valve core opening change, cause hydraulic cylinder to shake,
This can cause the violent shake of host, seriously affect on the long-armed implement such as high-altitude operation vehicle or concrete mixer
Job safety and homework precision.The pressure reducing circuit of pilot control level composition, some oil is directly to flow back to fuel tank, this is big
In flow system, the also no great influence of this oil return, but the guide's hand formed in small flow system or by accumulator
In handle control loop, the flow loss that fuel tank is flowed back in this part is very big, seriously limits the application of this invention.
4th, valve pocket is monolithic construction, when the processing of plug-in opening concentricity is bad excessive with installation moment of torsion, can be caused
Valve pocket deforms, and causes balance valve core and control piston to be blocked, reduces the reliability used.
The content of the invention
The technical problems to be solved by the invention be for above-mentioned state of the art and provide it is a kind of it is simple and reasonable,
Can stability contorting balance valve core aperture, from load disturbance, allow it is larger installation moment of torsion balanced valve.
Technical solution is used by the present invention solves above-mentioned technical problem：A kind of balanced valve, it is characterised in that：Including tool
There is the valve body of spool chamber, the first hydraulic fluid port to communicate with each other, the second hydraulic fluid port are provided with valve body, control port is also provided with valve body, the
One hydraulic fluid port and the second hydraulic fluid port are located on body wall, and control port is then located at valve body front end；Valve pocket is balanced, installed in valve body
In spool chamber, balance and be equipped with sealing ring between valve pocket periphery and spool cavity wall, balanced valve put on be provided with the second hydraulic fluid port of connection with
The import of the control chamber of valve pocket is balanced, balancing the front portion of the control chamber of valve pocket, there is omoplate in annular to form the first valve port, balance
First cross-sectional area of the control chamber of valve pocket is more than the second cross-sectional area of the first valve port；And can be opposite in balance valve pocket
The balance valve core of axial slip, balance valve core inside have ladder hole, and the control chamber that balance valve core will be balanced in valve pocket separates
Into independent ante-chamber and back cavity two parts, the second hydraulic fluid port is connected by balancing the 4th damping hole in sleeve side wall with the back cavity
Logical, the first valve port is stretched into the front end of balance valve core, and the rear end of balance valve core and the internal chamber wall of balance valve pocket coordinate, balance valve core
It is connected between rear end and front end by first conical surface, first conical surface is blocking the first valve port；The shifting state before balance valve core
Under, first conical surface is contacted with the first valve port, blocks the first hydraulic fluid port to be connected by the first valve port with the second hydraulic fluid port, after balance valve core
Under shifting state, first conical surface leaves the first valve port, and the first hydraulic fluid port is connected by the first valve port with the second hydraulic fluid port；Installed in balanced valve
In the ladder hole of core and the pilot valve that can slide to axial, pilot valve hold holding reach trend by the first spring,
Pilot valve periphery has second conical surface coordinated with the small-bore portion of ladder hole, and second conical surface is blocking ladder hole
Small-bore portion, the front end of pilot valve are located in the small-bore portion of ladder hole, and the rear end of pilot valve is located at ladder hole
In heavy caliber portion, in the rear end of pilot valve be equipped with to connect back cavity and ladder hole small-bore portion the 3rd damping hole,
The throttling channel become larger by rear to preceding flow area is provided with the front end periphery wall of the pilot valve；Move forward in pilot valve
Under state, second conical surface is contacted with the small-bore portion of ladder hole, blocks back cavity via the small of the 3rd damping hole and ladder hole
Behind the portion of aperture with the connection of the first hydraulic fluid port, after pilot valve under shifting state, back cavity successively via the 3rd damping hole, throttling channel and
Connected behind the small-bore portion of ladder hole with the first hydraulic fluid port；Pilot control part, push away the pressure oil by control port
Dynamic pilot valve movement.
As an improvement, the front end periphery of above-mentioned balance valve core is provided with to make the second hydraulic fluid port via the first valve port and the first oil
The linking runner that mouth communicates.So moved after balance valve core, the second hydraulic fluid port is communicated via linking runner with the first hydraulic fluid port, control
Pass through the flow velocity of the first valve port, it is ensured that work is more steady.
For convenience of the first spring is installed, the first spring base is equipped with above-mentioned back cavity, first spring is held in pilot valve
Between the rear end of core and the first spring base.
Further improve, above-mentioned valve body is by valve casing and passes through connector sleeve group of the buckle structure floating connection in valve casing rear end
Into.So that valve body forms floating connecting structure, by buckle structure by valve casing and connector sleeve floating connection, so in big installation
In the case that moment of torsion or plug-in opening working axiality are bad, the deformation of connector sleeve will not be transferred to balance valve pocket, pilot valve
And following control pistons, improve the reliability that balanced valve works.
3rd damping hole is for the benefit of set, equipped with connecting back cavity and ladder hole in the rear end of above-mentioned pilot valve
Second interface channel in small-bore portion, the second interface channel internal thread are connected with the 3rd damping block, and the 3rd damping hole is set
On the 3rd damping block.
Further improve, above-mentioned pilot control part includes the plunger shaft arranged on valve inner rear end, the front end of valve body
It is fixed with the end cap for blocking plunger shaft, has connection extraneous in end cap and the liquid outlet channel of plunger shaft, liquid outlet channel passes through the
Two valve ports are connected with plunger shaft, and the control port is arranged on end cap；First damping hole, is arranged in control port, and first
Damping hole connects extraneous and described plunger shaft；Nonreturn valve core, and can be single with respect to liquid outlet channel axial slip in liquid outlet channel
Held to spool by second spring to keep blocking the trend of the second valve port；And can opposing pistons chamber axial direction in plunger shaft
The control piston of sliding, is equipped with sealing ring and seals between the head of control piston and the inner hole wall of plunger shaft, the head of control piston
Plunger shaft is divided into rod chamber and rodless cavity two parts by portion, is equipped with control piston to connect the second of rod chamber and rodless cavity
Damping hole, the bar portion of control piston are pierced by the roof of rod chamber to promote the pilot valve, and the bar portion of control piston is with having
It is equipped with sealing ring between the roof inner hole wall of rod cavity to seal, to block rod chamber to connect with the spool chamber of valve body；3rd spring, if
In in rod chamber and act on control piston head make control piston keep towards end cap direction axial movement trend.
The advantages of foregoing pilot control part, is：
1), when from control port enter pilot control valve oil pressure px fly up when, fluid first by the first damping hole into
Enter in the rodless cavity of plunger shaft, the rising promotion control piston of pressure p1 moves to right in rodless cavity；When entering guide from control port
The oil pressure px of control valve is raised suddenly, and the fluid in rod chamber must be discharged to by moving to right for control piston via the second damping hole
In rodless cavity, control piston could continue to move to right, because of the presence of the second damping hole, pressure when control piston moves to right in rod chamber
P2 is more than pressure p1 in rodless cavity, and the pressure p 2 in rod chamber, which plays, prevents moving to right for control piston, realizes buffering；Only when
Control pressure px persistently rises, and control piston could continue to move to right, and plays the filter action to control pressure fluctuation.Similarly,
When the oil pressure px for entering pilot control valve from control port declines, pressure p1 in the pressure p 2 and rodless cavity in rod chamber
Decline (equilibrium state when p1=p2) at the same time, the decline of pressure p2 in rod chamber, reduce that pressure p1 in rodless cavity overcomes to
Right resistance, plays the role of cushioning control piston and moves to left.
2) but because need not be too big when balanced valve will close buffering, pass through matching somebody with somebody for nonreturn valve core and second spring
Close, can control in rodless cavity that pressure p1 and control pressure px are when certain pressure difference is reached, pressure p1 pressure in rodless cavity
Quickly opened by nonreturn valve core, via pressure release is expelled directly out after liquid outlet channel, without being put down via the first damping hole, final realize
The quick closedown of weighing apparatus valve.The advantages of foregoing pilot control part, is：
First damping hole is for the benefit of set, the control port internal thread of above-mentioned end cap is connected with the first damping block, and described
One damping hole is arranged on the first damping block.
Second damping hole is for the benefit of set, and the second connection that connection rod chamber and rodless cavity are equipped with above-mentioned control piston is logical
Road, the second interface channel internal thread are connected with the second damping block, and second damping hole is arranged on the second damping block.
Nonreturn valve core is for the benefit of assembled, second spring seat, the second spring top are equipped with the liquid outlet channel of above-mentioned end cap
Hold between second spring seat and nonreturn valve core.
Further improve, above-mentioned end cap has the threaded connection column portion for being inserted into and being threaded in plunger shaft, and screw thread connects
The annular wall for having on the rear end face in column portion and extending to control piston direction is connect, annular wall connects to the head with control piston
Touch.Because lug boss is stretched into plunger shaft, thus the length of control piston can do it is short, it is ensured that the afterbody of control piston can stretch into
It is cost-effective in heavy caliber portion, such as without column portion is threadedly coupled, then to ensure control piston afterbody stretch out plunger shaft could be into
Enter in heavy caliber portion, even if in addition the setting of annular wall ensures that control piston head is contacted with the annular wall of end cap, also ensure nothing
Rod cavity has certain space.
Compared with prior art, the advantage of the invention is that：
1st, the throttling channel become larger by rear to preceding flow area section is provided with the front end periphery wall of pilot valve, to realize
Flow gradual change, so makees or opens moment in fine motion, flow is moderate change, will not cause unexpected opening impact；
2nd, the open amount of balance valve core is controlled by pilot valve open amount, when pilot valve open certain distance,
The fluid of second hydraulic fluid port B reaches back cavity through the 4th damping hole, then via the 3rd damping hole, pilot valve throttling channel after flow into the
One hydraulic fluid port A, so has certain pressure differential, the pressure of the second hydraulic fluid port in the pressure p B pressure of the second hydraulic fluid port with the pressure p 3 in back cavity
Power pB>Pressure p 3 in back cavity, the pressure p B of the second hydraulic fluid port act on the annulus area A12 that balance valve core is formed by A1 and A2
On, the pressure p 3 in back cavity is acted in balance valve core in the first cross-sectional area A 1, so when pilot valve is opened to a spacing
From when, pB*A12>PB*A1, balance valve core are made a concerted effort to move right；But balance valve core one moves right so that pilot valve opening
Reduce (throttling channel effect) again, p3 rises again, until pb*A34=Pb*A3.The 3rd damping hole in pilot valve, in a level pressure
There is pressure compensation, it is ensured that balance valve flow is stablized in the range of power.This servo-actuated principle is so based on, is balanced
The opening of spool is the influence from load pressure, is only determined by the amount of exercise of pilot valve, so will not change because of load
Flowed fluctuation is caused, produces vibration.
3rd, valve body is floating connection form, will not be excessive or valve opening machining accuracy not enough causes spool because of installation moment of torsion
It is stuck, improve reliability.
Brief description of the drawings
Fig. 1 is the structure sectional view of the embodiment of the present invention；
Fig. 2 is the sectional view that valve pocket is balanced in the embodiment of the present invention；
Fig. 3 is the front view of balance valve core in the embodiment of the present invention；
Fig. 4 is the side view of balance valve core in the embodiment of the present invention；
Fig. 5 is the front view of pilot valve in the embodiment of the present invention；
Fig. 6 is the side view of pilot valve in the embodiment of the present invention；
Fig. 7 is the structure sectional view of pilot control part in the embodiment of the present invention；
Fig. 8 is the principle schematic of pilot control part in the embodiment of the present invention；
Fig. 9 is the application principle schematic diagram of the embodiment of the present invention；
Figure 10 is that the common load using balanced valve being currently used in the boom system of concrete mixer controls hydraulic pressure
System.
Embodiment
The present invention is described in further detail below in conjunction with attached drawing embodiment.
It is a preferred embodiment of the present invention as shown in Fig. 1~9.
A kind of balanced valve, including
Valve body 1 with spool chamber, is provided with the first hydraulic fluid port A to communicate with each other, the second hydraulic fluid port B on valve body 1, on valve body 1 also
It is provided with control port X, the first hydraulic fluid port A and the second hydraulic fluid port B to be located on body wall, control port X is then located at 1 front end of valve body.
Valve body 1 is formed by valve casing 12 and by connector sleeve 14 of 13 floating connection of buckle structure in 12 rear end of valve casing.
Valve pocket 2 is balanced, in the spool chamber of valve body 1, balances and sealing is equipped between 2 periphery of valve pocket and spool cavity wall
Circle, balances the import 21 for the control chamber that the second hydraulic fluid port B of connection is provided with valve pocket 2 and balances valve pocket 2, balances the control chamber of valve pocket 2
Front portion there is omoplate 22 in annular to form the first valve port 4a, the first cross-sectional area A 1 for balancing the control chamber of valve pocket 2 is more than the
The second cross-sectional area A 2 of one valve port 4a.
Balance valve core 3 that is interior installed in balance valve pocket 2 and can sliding to axial, the inside of balance valve core 3 leads to ladder
The control chamber balanced in valve pocket 2 is separated into independent ante-chamber 5a and back cavity 5b two parts by hole, balance valve core 3, and the second hydraulic fluid port B leads to
The 4th damping hole 7d on 2 side wall of overbalance valve pocket is connected with back cavity 5b, and the first valve port 4a is stretched into the front end 31 of balance valve core 3,
The rear end 32 of balance valve core 3 and the internal chamber wall of balance valve pocket 2 coordinate, by the between the rear end 32 and front end 31 of balance valve core 3
One conical surface 33 is connected, and first conical surface 33 is blocking the first valve port 4a.31 periphery of front end of balance valve core 3 is provided with to make
The linking runner 311 that two hydraulic fluid port B are communicated via the first valve port 4a with the first hydraulic fluid port A.
Before balance valve core 3 under shifting state, first conical surface 33 is contacted with the first valve port 4a, blocks the first hydraulic fluid port A by the
One valve port 4a is connected with the second hydraulic fluid port B, and after balance valve core 3 under shifting state, first conical surface 33 leaves the first valve port 4a, the
One hydraulic fluid port A is connected by the first valve port 4a with the second hydraulic fluid port B.
In the ladder hole of balance valve core 3 and the pilot valve 8 that can slide to axial, pilot valve 8 is by
One spring 10a, which is held, keeps reach trend, and the first spring base 11a is equipped with back cavity 5b, and the first spring 10a is held in pilot valve
Rear end and the first spring base 11a between.8 periphery of pilot valve has the second cone coordinated with the small-bore portion 34 of ladder hole
Face 81, for second conical surface 81 to block the small-bore portion 34 of ladder hole, the front end of pilot valve 8 is located at the aperture of ladder hole
In footpath portion 34, the rear end of pilot valve 8 is located in the heavy caliber portion 35 of ladder hole, in the rear end of pilot valve 8 be equipped with to
The 3rd damping hole 7c in the small-bore portion 34 of back cavity 5b and ladder hole is connected, is opened on the front end periphery wall of the pilot valve 8
There are the throttling channel 82 become larger by rear to preceding flow area, 82 triangular shape of throttling channel.
Before pilot valve 8 under shifting state, second conical surface 81 is contacted with the small-bore portion 34 of ladder hole, blocks back cavity 5b
Via the connection behind the small-bore portion 34 of the 3rd damping hole 7c and ladder hole with the first hydraulic fluid port A, the shifting state after pilot valve 8
Under, back cavity 5b connects via behind the small-bore portion 34 of the 3rd damping hole 7c, throttling channel 82 and ladder hole with the first hydraulic fluid port A successively
It is logical.In the rear end of pilot valve 8 be equipped with to connect back cavity 5b and ladder hole small-bore portion 34 the second interface channel 83,
Second interface channel, 83 internal thread is connected with the 3rd damping block 73, and the 3rd damping hole 7c is arranged on the 3rd damping block 73.
Pilot control part, to make the pressure oil by control port X promote pilot valve 8 to move.
Pilot control part includes
Arranged on the plunger shaft 15 of 1 Internal back end of valve body, valve body 1 is fixedly arranged at the front end with the end cap 6 for blocking plunger shaft 15, end
There is the liquid outlet channel 61 for connecting extraneous and described plunger shaft 15, liquid outlet channel 61 passes through the second valve port 4b and plunger shaft in lid 6
15 connections, control port X are arranged on 6 on end cap.
First damping hole 7a, is arranged in control port X, the first damping hole 7a connections external world and plunger shaft 15.End cap 6
Control port X internal threads are connected with the first damping block 71, and the first damping hole 7a is arranged on the first damping block 71.
Nonreturn valve core 16, and can be with respect to 61 axial slip of liquid outlet channel, the nonreturn valve core in the liquid outlet channel 61
16 are held by second spring 10b to keep blocking the trend of the second valve port 4b；The second bullet is equipped with the liquid outlet channel 61 of end cap 6
Spring abutment 11b, the second spring 10b are held between second spring seat 11b and nonreturn valve core 16.
In the plunger shaft 15 and can 15 axial slip of opposing pistons chamber control piston 9, the head 91 of control piston 9 and
It is equipped with sealing ring between the inner hole wall of plunger shaft 15 to seal, the head 91 of control piston 9 divides plunger shaft 15 for 151 He of rod chamber
152 two parts of rodless cavity, control piston 9 is interior to be equipped with to connect the second damping hole 7b of rod chamber 151 and rodless cavity 152, control
The bar portion 92 of piston 9 processed is pierced by the roof of rod chamber 151 to promote the pilot valve 8, and the bar portion 92 of control piston 9 is with having
It is equipped with sealing ring between the roof inner hole wall of rod cavity 151 to seal, to block rod chamber 151 and the spool chamber of valve body 1 to connect；End cap
6 have the threaded connection column portion 63 for being inserted into and being threaded in plunger shaft 15, and being threadedly coupled on the rear end face in column portion 63 has
The annular wall 62 extended to 9 direction of control piston, annular wall 62 contact to the head 91 with control piston.In control piston 9
The second interface channel 93 equipped with connection rod chamber 151 and rodless cavity 152,93 internal thread of the second interface channel are connected with the second resistance
Buddhist nun's block 72, the second damping hole 7b are arranged on the second damping block 72.
3rd spring 10c, in the rod chamber 151 and acting on the head 91 of control piston 9 makes control piston 9 keep court
The trend of 6 direction of end cap axial movement.
The operation principle and process of this balanced valve are divided into rising, stop, and decline 3 processes, as shown in Figure 9.
Uphill process, the pressure oil promotion that the pressure oil of reversal valve reaches the first hydraulic fluid port A, the first hydraulic fluid port A of balanced valve are flat
Weighing apparatus spool 12 is opened (at this moment pilot valve 8 is closed mode), and the first oil flows into the second hydraulic fluid port B through A and reaches hydraulic cylinder rodless cavity,
Promote hydraulic cylinder uplink.
Decline process, the pressure oil of control port X promote control piston 15 to move to right, result from pilot valve 8 certain
Displacement, hydraulic cylinder are slowly declined by inactive state；Control port X pressure continues to increase, and the opening of pilot valve 8 continues to increase, liquid
Cylinder pressure speed continues to increase；When 8 displacement of pilot valve continues to increase to certain phase in control port X pressure, balance valve core 3 is opened
Open, the open amount of balance valve core 3 is controlled by 8 open amount of pilot valve, when pilot valve 8 open certain distance, second
The fluid of hydraulic fluid port B through the 4th damping hole 7d reach back cavity 5b, then via the 3rd damping hole 7c, pilot valve throttling channel 82 after flow
Enter the first hydraulic fluid port A, so have certain pressure differential, the second hydraulic fluid port with the pressure p 3 in back cavity in the pressure p B pressure of the second hydraulic fluid port
Pressure p B>Pressure p 3 in back cavity, the pressure p B of the second hydraulic fluid port act on the annulus area that balance valve core is formed by A1 and A2
On A12, the pressure p 3 in back cavity is acted in balance valve core in the first cross-sectional area A 1, so when pilot valve is opened to certain
Apart from when, pB*A12>PB*A1, balance valve core are made a concerted effort to move right；But balance valve core 3 one moves right so that pilot valve 8
Opening reduces (throttling channel 82 acts on) again, and p3 rises again, until pb*A34=Pb*A3.The 3rd damping hole 7c in pilot valve,
There is pressure compensation in the range of certain pressure, it is ensured that balance valve flow is stablized.Because the setting of throttling channel 82 is realized
Flow gradual change, so makees or opens moment in fine motion, flow is moderate change, will not cause unexpected opening impact.By control oil
The opening of mouth X pressure controllables balance valve core 3, so that the speed speed that control cylinder declines.So it is based on this servo-actuated
Principle, the opening of balance valve core are the influences from load pressure, are only determined by the amount of exercise of pilot valve, so will not be because of
Load change causes flowed fluctuation, produces vibration.
Stopped process, control port x pressure reduce, and pilot valve 8 reduces displacement, between pilot valve 8 and balance valve core 3
82 area of throttling channel of formation reduces, and balances end pressure increase after main valve plug 3, and balance valve core 3 moves forward；Control port x pressure drops
For 0, pilot valve 8 is pushed forward by the first spring 10a, and second conical surface 71 is so flat to block the small-bore portion 34 of ladder hole
Spool 3 weigh under the action of the second hydraulic fluid port B pressure, the realization that also travels forward is closed.
The operation principle and process of this pilot control valve are as follows：
1st, when the pilot valve of balanced valve reaches balanced steady state, the oil of pilot control valve is entered from control port X
Press the pressure p 2 in the pressure p 1=rod chambers 151 in px=rodless cavities 152, the opening of pilot valve 8 in balanced valve is stablized, control
5 position of piston processed is fixed.
2nd, when the oil pressure px for entering pilot control valve from control port X is flown up, fluid is first by the first damping hole 7a
Into in the rodless cavity 151 of plunger shaft, the rising promotion control piston 9 of pressure p1 moves to right in rodless cavity 151；When from control port
The 62 oil pressure px for entering pilot control valves are raised suddenly, and moving to right for control piston 9 must be by the fluid in rod chamber 152 via the
Two damping hole 7b are discharged in rodless cavity 151, and control piston 9 could continue to move to right, and because of the presence of the second damping hole 7b, control is lived
Pressure p 2 of the plug 9 when moving to right in rod chamber 152 is more than pressure p1 in rodless cavity 151, and the pressure p 2 in rod chamber 152 plays prevention
Control piston 9 moves to right, and realizes buffering；Only when control pressure px persistently rises, control piston 9 could continue to move to right, and rise
The filter action to control pressure fluctuation is arrived.Similarly, when from control port X enter pilot control valve oil pressure px decline when
Wait, pressure p1 declines (equilibrium state when p1=p2), rod chamber 152 at the same time in the pressure p 2 and rodless cavity 151 in rod chamber 152
The decline of interior pressure p2, reduces the resistance to the right that pressure p1 in rodless cavity 151 overcomes, and plays cushioning control piston 9 and moves to left
Effect.
3 but because need not be too big when balanced valve will close buffering, pass through nonreturn valve core 16 and second spring 10b
Cooperation, can control in rodless cavity 151 that pressure p1 and control pressure px are when certain pressure difference is reached, in rodless cavity 151
1 pressure of pressure p is quickly opened by nonreturn valve core 16, via pressure release is expelled directly out after liquid outlet channel 61, without via the first resistance
Buddhist nun hole 7a, finally realizes the quick closedown of balanced valve.
Although the preferred embodiment of the present invention described in detail above, it is to be clearly understood that for this area
Technical staff for, the invention may be variously modified and varied.That is made within the spirit and principles of the invention appoints
What modification, equivalent substitution, improvement etc., should all be included in the protection scope of the present invention.
Claims (10)
- A kind of 1. balanced valve, it is characterised in that：IncludingValve body (1) with spool chamber, is provided with the first hydraulic fluid port (A) to communicate with each other, the second hydraulic fluid port (B), valve body on valve body (1) (1) control port (X) is also provided with, first hydraulic fluid port (A) and the second hydraulic fluid port (B) are located on body wall, control port (X) Then it is located at valve body (1) front end；Valve pocket (2) is balanced, in the spool chamber of valve body (1), is balanced between valve pocket (2) periphery and spool cavity wall equipped with close Seal, balances the import (21) for the control chamber that the second hydraulic fluid port of connection (B) and balance valve pocket (2) are provided with valve pocket (2), balances valve pocket (2) there is omoplate (22) in annular to form the first valve port (4a) for the front portion of control chamber, balance the first of the control chamber of valve pocket (2) Cross-sectional area (A1) is more than the second cross-sectional area (A2) of the first valve port (4a)；Installed in the balance valve core (3) that balance valve pocket (2) is interior and can slide to axial, there is ladder inside balance valve core (3) The control chamber balanced in valve pocket (2) is separated into independent ante-chamber (5a) and back cavity (5b) two parts by through hole, balance valve core (3), Second hydraulic fluid port (B) is connected by balancing the 4th damping hole (7d) on valve pocket (2) side wall with back cavity (5b), balance valve core (3) The first valve port (4a) is stretched into front end (31), and the rear end (32) of balance valve core (3) coordinates with the internal chamber wall of balance valve pocket (2), balance It is connected between the rear end (32) and front end (31) of spool (3) by first conical surface (33), first conical surface (33) is blocking the One valve port (4a)；Before balance valve core (3) under shifting state, first conical surface (33) contacts with the first valve port (4a), blocks the first hydraulic fluid port (A) connected by the first valve port (4a) with the second hydraulic fluid port (B), under balance valve core (3) afterwards shifting state, first conical surface (33) The first valve port (4a) is left, the first hydraulic fluid port (A) is connected by the first valve port (4a) with the second hydraulic fluid port (B)；In the ladder hole of balance valve core (3) and the pilot valve (8) that can slide to axial, pilot valve (8) by First spring (10a) holds the reach trend that keeps, and pilot valve (8) periphery has to be coordinated with the small-bore portion (34) of ladder hole Second conical surface (81), second conical surface (81) is to block the small-bore portion (34) of ladder hole, the front end position of pilot valve (8) In the small-bore portion (34) of ladder hole, the rear end of pilot valve (8) is located in the heavy caliber portion (35) of ladder hole, guide In the rear end of spool (8) be equipped with to connect back cavity (5b) and ladder hole small-bore portion (34) the 3rd damping hole (7c), The throttling channel (82) become larger by rear to preceding flow area is provided with the front end periphery wall of the pilot valve (8)；Before pilot valve (8) under shifting state, second conical surface (81) is contacted with the small-bore portion (34) of ladder hole, blocks back cavity (5b) via the connection with the first hydraulic fluid port (A) afterwards of the small-bore portion (34) of the 3rd damping hole (7c) and ladder hole, in pilot valve Core (8) is afterwards under shifting state, and back cavity (5b) is successively via the small-bore portion of the 3rd damping hole (7c), throttling channel (82) and ladder hole (34) connected afterwards with the first hydraulic fluid port (A)；Pilot control part, to make the pressure oil by control port (X) promote pilot valve (8) mobile.
- 2. balanced valve according to claim 1, it is characterised in that：Front end (31) periphery of the balance valve core (3) is provided with To make the linking runner (311) that the second hydraulic fluid port (B) is communicated via the first valve port (4a) with the first hydraulic fluid port (A).
- 3. balanced valve according to claim 1, it is characterised in that：The first spring base (11a) is equipped with the back cavity (5b), First spring (10a) is held between the rear end of pilot valve and the first spring base (11a).
- 4. balanced valve according to claim 1, it is characterised in that：The valve body (1) is by valve casing (12) and passes through buckle structure (13) connector sleeve (14) of the floating connection in valve casing (12) rear end forms.
- 5. balanced valve according to claim 1, it is characterised in that：It is equipped with the rear end of the pilot valve (8) to connect Second interface channel (83) in the small-bore portion (34) of back cavity (5b) and ladder hole, the connection of the second interface channel (83) internal thread There is the 3rd damping block (73), the 3rd damping hole (7c) is arranged on the 3rd damping block (73).
- 6. according to the balanced valve described in Claims 1 to 5 any claim, it is characterised in that：The pilot control part bag IncludeArranged on the plunger shaft (15) of valve body (1) Internal back end, valve body (1) is fixedly arranged at the front end with the end cap for blocking plunger shaft (15) (6), there is the liquid outlet channel (61) for connecting extraneous and described plunger shaft (15), liquid outlet channel (61) passes through second in end cap (6) Valve port (4b) is connected with plunger shaft (15), and the control port (X) is arranged on end cap (6)；First damping hole (7a), is arranged in control port (X), the first damping hole (7a) connection external world and plunger shaft (15)；Nonreturn valve core (16), and can be with respect to liquid outlet channel (61) axial slip, the check valve in the liquid outlet channel (61) Core (16) is held by second spring (10b) to keep blocking the trend of the second valve port (4b)；In the plunger shaft (15) and can opposing pistons chamber (15) axial slip control piston (9), the head of control piston (9) (91) it is equipped with sealing ring between the inner hole wall of plunger shaft (15) to seal, the head (91) of control piston (9) is by plunger shaft (15) It is divided into rod chamber (151) and rodless cavity (152) two parts, is equipped with control piston (9) to connect rod chamber (151) and without bar The second damping hole (7b) of chamber (152), the bar portion (92) of control piston (9) are pierced by the roof of rod chamber (151) to promote Pilot valve (8) is stated, it is close that sealing ring is equipped between the bar portion (92) of control piston (9) and the roof inner hole wall of rod chamber (151) Envelope, to block rod chamber (151) and the spool chamber of valve body (1) to connect；3rd spring (10c), in the rod chamber (151) and acts on the heads (91) of control piston (9) and makes control piston (9) Keep the trend towards the axial movement of end cap (6) direction.
- 7. balanced valve according to claim 6, it is characterised in that：Control port (X) internal thread of the end cap (6) is connected with First damping block (71), first damping hole (7a) are arranged on the first damping block (71).
- 8. balanced valve according to claim 6, it is characterised in that：Connection rod chamber (151) is equipped with the control piston (9) With the second interface channel (93) of rodless cavity (152), the second interface channel (93) internal thread is connected with the second damping block (72), institute The second damping hole (7b) is stated to be arranged on the second damping block (72).
- 9. balanced valve according to claim 6, it is characterised in that：Second is equipped with the liquid outlet channel (61) of the end cap (6) Spring base (11b), the second spring (10b) are held between second spring seat (11b) and nonreturn valve core (16).
- 10. balanced valve according to claim 6, it is characterised in that：The end cap (6), which has, is inserted into and is threaded in piston Threaded connection column portion (63) in chamber (15), is threadedly coupled to have on the rear end face of column portion (63) and prolongs to control piston (9) direction The annular wall (62) stretched, annular wall (62) contact to the head (91) with control piston.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610559900.9A CN105952705B (en) | 2016-06-29 | 2016-06-29 | Balanced valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610559900.9A CN105952705B (en) | 2016-06-29 | 2016-06-29 | Balanced valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105952705A CN105952705A (en) | 2016-09-21 |
| CN105952705B true CN105952705B (en) | 2018-05-04 |
Family
ID=56900070
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610559900.9A Active CN105952705B (en) | 2016-06-29 | 2016-06-29 | Balanced valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105952705B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108709000A (en) * | 2018-08-22 | 2018-10-26 | 佛山信卓派思机械科技有限公司 | A kind of flow type balanced valve of setting pressure automatic adjustment |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106931169B (en) * | 2017-04-17 | 2023-07-21 | 天津华宁电子有限公司 | Mining electromagnetic pilot valve core |
| CN108105193B (en) * | 2017-12-21 | 2019-11-22 | 浙江达柏林阀门有限公司 | A kind of balanced valve that can reduce Glais ring frictional force |
| CN108443269B (en) * | 2018-03-23 | 2023-07-28 | 浙江迦南科技股份有限公司 | Unidirectional speed limiting device |
| CN108974294B (en) * | 2018-07-28 | 2023-09-29 | 华中科技大学 | Buoyancy adjusting system based on two-way sea water pump |
| CN108869434B (en) * | 2018-09-21 | 2019-11-26 | 浙江达柏林阀门有限公司 | A kind of balanced valve |
| CN109373012B (en) * | 2018-12-03 | 2023-09-15 | 四川理工学院 | Micro-flow equal-flow diverter valve |
| CN111664136B (en) * | 2020-05-25 | 2024-04-19 | 圣邦集团有限公司 | Load compensation balance valve |
| CN111720381B (en) * | 2020-06-29 | 2022-07-15 | 潍柴动力股份有限公司 | Balance valve, hydraulic control system and engineering machinery |
| CN113915184B (en) * | 2021-09-13 | 2024-05-03 | 烟台艾迪液压科技有限公司 | Balance valve with reversing throttling function |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5409040A (en) * | 1993-08-09 | 1995-04-25 | Koomey Companies International, Inc. | Springless pilot operated sequence valve |
| CN2804450Y (en) * | 2005-06-01 | 2006-08-09 | 刘恒海 | Balancing valve |
| CN101852222B (en) * | 2009-03-31 | 2012-11-21 | 徐州重型机械有限公司 | Balanced valve and crane using same |
| CN102072215B (en) * | 2011-02-02 | 2012-11-28 | 卢宇 | Balance valve with quickly-closing valve plug |
| CN202811595U (en) * | 2012-09-24 | 2013-03-20 | 温州美瑞克液压有限公司 | Novel thread plug-in mounting type split shuttle valve |
-
2016
- 2016-06-29 CN CN201610559900.9A patent/CN105952705B/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108709000A (en) * | 2018-08-22 | 2018-10-26 | 佛山信卓派思机械科技有限公司 | A kind of flow type balanced valve of setting pressure automatic adjustment |
| CN108709000B (en) * | 2018-08-22 | 2019-11-15 | 浙江斯丹特阀门股份有限公司 | A kind of flow type balanced valve of setting pressure automatic adjustment |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105952705A (en) | 2016-09-21 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105952705B (en) | Balanced valve | |
| CN106195370B (en) | Cartridge balanced valve | |
| CN106015140B (en) | A kind of balanced valve | |
| CN106050775B (en) | Structure improved pilot-actuated valve | |
| CN101629587B (en) | Hydraulic balance valve | |
| CN202732526U (en) | Combined hydraulic balance valve | |
| CN201653131U (en) | Hydraulic lifting system for walking beam of large-sized walking beam furnace | |
| CN105952703B (en) | Thread cartridge balanced valve | |
| CN103591075B (en) | Hydraulic control system synchronous with crane and balancing weight hydraulic cylinder | |
| CN204704176U (en) | A kind of piston elevator mechanism and hydraulic control device thereof | |
| CN100441885C (en) | Hydraulic balance valve capable of automatically adapting load change | |
| CN104879334B (en) | Piston elevating mechanism and its hydraulic control device | |
| CN105971956B (en) | A kind of pilot-actuated valve | |
| CN106969000A (en) | A kind of engineering truck shift operating device hydraulic buffering valve | |
| CN104533863B (en) | Crane rotation system control valve | |
| CN104609321B (en) | A kind of crane arm support hydraulic control system with adjustable amplitude, luffing device and crane | |
| CN103573735A (en) | Pilot large-flow load control valve using displacement and force feedback principle | |
| CN103104565A (en) | Balance valve | |
| CN107725523A (en) | Load sensing multi-way valve and there is its engineering machinery | |
| CN101725743B (en) | Balance valve | |
| CN111828420B (en) | Hydraulic compensation balance valve | |
| CN104747523B (en) | A kind of lowering velocity limits hydraulic control valve | |
| CN105179361B (en) | A kind of hydraulic cushion oil cylinder and crane | |
| CN108775431A (en) | Balanced valve | |
| CN203548397U (en) | Pilot high-flow load control valve based on displacement-force feedback principle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| CB03 | Change of inventor or designer information | ||
| CB03 | Change of inventor or designer information |
Inventor after: Zhou Zhongyong Inventor before: Chen Yanyan |
|
| TA01 | Transfer of patent application right | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20180408 Address after: 224400 Central Road, Funing Economic Development Zone, Yancheng City, Jiangsu Province, No. 2 Applicant after: JIANGSU JINGWEI VALVE CO., LTD. Address before: 315000 Zhejiang city of Ningbo province high tech Zone Juxian Road No. 555 building 035 room 18-1 013 station Applicant before: Ningbo Wen fan electrical and Mechanical Technology Development Co., Ltd. |
|
| GR01 | Patent grant | ||
| GR01 | Patent grant |