CN105971965A - Flow type balancing valve - Google Patents
Flow type balancing valve Download PDFInfo
- Publication number
- CN105971965A CN105971965A CN201610578641.4A CN201610578641A CN105971965A CN 105971965 A CN105971965 A CN 105971965A CN 201610578641 A CN201610578641 A CN 201610578641A CN 105971965 A CN105971965 A CN 105971965A
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- Prior art keywords
- valve
- hole
- hydraulic fluid
- fluid port
- main valve
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Classifications
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- 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
- F15B13/023—Excess flow valves, e.g. for locking cylinders in case of hose burst
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- 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
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
- F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
- F16K11/0716—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides with fluid passages through the valve member
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- 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
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/0473—Multiple-way safety valves
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Multiple-Way Valves (AREA)
- Sliding Valves (AREA)
Abstract
The invention discloses a flow type balancing valve which comprises a valve body, a main valve element, a one-way valve element, a guide valve sleeve assembly, a first elastic piece and a second elastic piece. The guide valve sleeve assembly is fixedly connected with the valve body in a sleeved mode in the opposite direction, the main valve element and the one-way valve element slide oppositely in the axial direction and are arranged in the guide valve sleeve assembly, the valve body is provided with an oil opening X, the guide valve sleeve assembly forms an oil opening V and an oil opening C, and the oil opening C is communicated with an inner cavity of the one-way valve element and a liquid flow channel in the main valve element; a plurality of throttling through holes are formed in the position, close to the oil opening V, of the guide valve sleeve assembly in the radial direction; when oil enters from the oil opening V, the one-way valve is switched on, and the oil opening V is communicated with the oil opening C; when oil enters from the oil opening X, the main valve element is pushed to be compressed in the axial direction and move towards the first elastic piece, the throttling through holes of the guide valve sleeve assembly are exposed, and the through-flow area is gradually increased. The flow type balancing valve is simpler in machining, smoother in overflowing, capable of precisely controlling the load lowering speed and reliable in use.
Description
Technical field
The present invention relates to control valve technical field, particularly relate to a kind of can accurately control and load lowering velocity
Flow type balanced valve.
Background technology
In the plant equipment such as the engineering machinery in modern times, building machinery, widely apply the hydraulic circuit that hoists, its
Middle balanced valve is to control the crucial Hydraulic Elements of hydraulic jack work, the quality of balanced valve performance in hoisting circuit
Directly affect the performance of main frame.Generally there is such a shortcoming in existing hydraulically balanced valve: when under load
When putting, owing to hydraulically balanced valve valve port area of passage can produce sudden change, load can be made to produce low frequency and to tremble
The dynamic phenomenon with impact, causes system unstable, affects the security reliability of complete machine.
Patent announcement number is CN103470815B, the patent of invention of entitled " balanced valve " provides one
The balanced valve of area of passage gradual change, its by mill out on poppet valve core groove that multiple width differs, aperture and
Inclined hole combines, and reaches the purpose of flow gradual change.But this design has the disadvantage in that
(1) what load was passed through when transferring and load rising is same valve port, all can produce restriction effect, and
In reality, load need not throttling action when rising, and has a strong impact on the efficiency of operation；Ask to solve this
Topic also needs a check valve in parallel, virtually adds expense；
(2), after milling out groove on poppet valve core and getting out aperture and inclined hole, the rigidity of spool is substantially reduced,
Control to bear bigger pressure reduction and quick liquid flow impact, if heat treatment is bad in addition, valve when load is transferred
Core is easy to drop, and reliability is substantially reduced；
(3) groove milling on poppet valve core, processed complex, efficiency are low, and therefore cost of manufacture is high；
(4) unlatching of spool is affected by load pressure, when loading the biggest, it is only necessary to the least control
Pressure just can allow valve port reach the biggest position, also can produce flow sudden change.
Summary of the invention
It is an object of the invention to overcome the defect of prior art, it is provided that a kind of flow type balanced valve, this balance
Valve processing is simpler, it is milder to cross stream, can accurately control to load lowering velocity, uses reliable.
For above technical problem, the technical solution of the present invention is to provide a kind of has following structure
Flow type balanced valve, this balanced valve includes: valve body, main valve plug, nonreturn valve core, guide valve grip assembly,
One elastic component and the second elastic component, guide valve grip assembly is the most fixedly sleeved with valve body, main valve plug and check valve
Core is axially towards one another and is slidably arranged in guide valve grip assembly, the first elastic component be located at valve body and main valve plug it
Between, the second elastic component is located between guide valve grip assembly and nonreturn valve core；Guide valve grip assembly is formed radially
V hydraulic fluid port and axial C hydraulic fluid port, V hydraulic fluid port is positioned at the junction of main valve plug and nonreturn valve core, C hydraulic fluid port with
Arrange in the inner chamber of nonreturn valve core and main valve plug fluid course connection；Guide valve grip assembly is near V oil
Opening's edge is radially provided with multiple throttling through hole.
When the non-oil-feed of V hydraulic fluid port, main valve plug and nonreturn valve core are at the first elastic component and the second elastic component in opposite directions
Close under active force thus cut off V hydraulic fluid port and C hydraulic fluid port.When V hydraulic fluid port oil-feed, nonreturn valve core is opened, V
Hydraulic fluid port connects with C hydraulic fluid port.Promote main valve plug vertically to compressing the first elastic component side when X hydraulic fluid port oil-feed
When mobile, the throttling through hole of guide valve grip assembly exposes, and flow area incrementally increases.Herein, guide valve
Grip assembly is the most fixedly sleeved with valve body refers to that guide valve grip assembly at least partial insertion valve body is interior and is formed
Fixing connection.Main valve plug and nonreturn valve core are axially towards one another in being slidably arranged in guide valve grip assembly and refer to, main
Spool and the axially opposed setting of nonreturn valve core, and by the way of being slidably matched, all it is located at guiding valve pocket group
Part.
Further, guide valve grip assembly mainly includes the first guide pin bushing, the second guide pin bushing and valve pocket, nonreturn valve core
Being located in one end of valve pocket, snap connection with valve body in the middle part of the other end of valve pocket, the other end of valve pocket is near end
Portion is connected by alignment pin with the second guide pin bushing, is formed with recessed position between the second guide pin bushing and valve body, and first leads
Set is connected to recessed position and some extends to body cavity direction.It is understood that first is elastic
Part is located in the first chamber that valve body and spool are formed, and one end of the first guide pin bushing is to valve inner or inner chamber (also
It is exactly the first chamber direction) extend, therefore, the motion to nonreturn valve core direction of first elastic component is led by first
Overlap the restriction of the distance that moves right to valve extension position and main valve plug.It addition, in a side of the present invention
In case, multiple throttling through holes are distributed in the position between V hydraulic fluid port and buckle.
Preferably, the second guide pin bushing includes shoulders and insertion section, and the front end of insertion section is provided with multiple first throttle
Through hole, the rear end of insertion section is provided with the first dowel hole, and valve pocket is provided with the multiple first throttles with insertion section
Multiple second section openings of through hole one_to_one corresponding connection and the corresponding with the first dowel hole second location
Pin-and-hole.
In a preferred embodiment, the diameter of first throttle through hole respectively with corresponding second section opening
Equal diameters.Owing to first throttle through hole and second section opening are one_to_one corresponding, therefore when not blocked,
The area of passage of the throttling through hole after the connection formed is exactly corresponding first throttle through hole or second section circulation
The area in hole.
In one embodiment, the first guide pin bushing is provided with the first oblique hole, the first oblique hole connection X hydraulic fluid port and
Second controls chamber；Second guide pin bushing is provided with the second oblique hole, and the second oblique hole connection V hydraulic fluid port and the 3rd controls
Chamber；Main valve plug is provided with the 3rd oblique hole and the 4th oblique hole, and the 3rd one end, oblique hole controls chamber phase with first
Logical, the one end in the other end and the 4th oblique hole communicates, and the other end in the 4th oblique hole and the 3rd controls chamber and communicates.
Further, nonreturn valve core is provided with the internal diameter of bell and bell more than court towards the side of main valve plug
To the main valve plug end face external diameter of nonreturn valve core side, under V hydraulic fluid port not oil-feed state, main valve plug is elastic first
Abut to the bell of nonreturn valve core under the effect of part and form linear sealing and cut off V hydraulic fluid port and C hydraulic fluid port.
Further, main valve plug includes being sequentially connected with back end cylindrical, first shoulder, the first recess, second
Shoulder and front end, front end is formed with the second recess at the second shoulder, the second control chamber is the second recess
It is connected formation with the first guide pin bushing and the second guide pin bushing；First recess connects first shoulder and the second shoulder, and first
Recess and the first guide pin bushing connect formation the first control chamber；There is the 3rd recess in the middle part of main valve plug leading portion, and the 3rd is recessed
Portion is connected formation the 3rd control chamber with the first valve pocket.
Preferably, main valve plug is provided with axial trumpet type hole towards one end of nonreturn valve core, on main valve plug also
It is provided with the first flow hole that one end connects and connect with the other end in first flow hole with trumpet type hole
Three oblique holes, the other end in the 3rd oblique hole is positioned at first shoulder and the back end cylindrical junction of main valve plug.
In a preferred embodiment, the aperture internal diameter in trumpet type hole and the equal diameters of back end cylindrical, front
The external diameter of end and the equal diameters of first shoulder, the diameter of the second shoulder is more than the diameter of first shoulder.
Beneficial effects of the present invention is as follows:
The flow type balanced valve of the present invention by arrange in a valve body nonreturn valve core and one for
The main valve plug of throttling, and by the way of throttling through hole is set on guide valve grip assembly, control bound core
Move and just can relatively accurately control area of passage so that do not limited by throttling when hydraulic cylinder rises, at liquid
Cylinder pressure is controlled by than shallower throttling when declining.Flow type balanced valve in the present invention is owing to need not picture
A lot of grooves equally processed by balanced valve of the prior art, and overall processing is simpler, and cross stream milder,
Can accurately control to load lowering velocity, use more reliable.
It addition, the fluid course in main valve plug is arranged, the fluid of C hydraulic fluid port is incorporated into the opposite side of main valve plug,
The pressure making C hydraulic fluid port acts on the active force on main valve plug two ends and can mutually balance, so that winner
The unlatching of spool is not the most by load effect.
Accompanying drawing explanation
For the technical scheme being illustrated more clearly that in the embodiment of the present invention, institute in embodiment being described below
The accompanying drawing used is needed to briefly introduce.It should be evident that drawings discussed below is only the one of the present invention
A little embodiments, from the point of view of those of ordinary skill in the art, on the premise of not paying creative work,
Other accompanying drawing can also be obtained according to these accompanying drawings.
Fig. 1 show the structural representation of the flow type balanced valve one of which embodiment of the present invention；
The principle schematic of the flow type balanced valve that Fig. 2 show in Fig. 1；
Fig. 3 show the principle schematic of the hydraulic circuit using inventive flow type balanced valve；
A kind of structural representation of the valve pocket that Fig. 4 show in Fig. 1；
A kind of structural representation of the second guide pin bushing that Fig. 5 show in Fig. 1.
In figure: 1, valve body, the 2, first elastic component, 3, spring base, the 4, first chamber, 5, first leads
Set, 6, first controls chamber, and 7, main valve plug, 7.1, first shoulder, the 7.2, second shoulder, the 8, second control
Chamber processed, the 9, second guide pin bushing, 10, alignment pin, 11, buckle, 12, valve pocket, 13, nonreturn valve core, 14,
Second elastic component, 15, first flow hole, the 16, the 4th oblique hole, the 17, second inclined hole, 18, first is oblique
Xiang Kong, 19, X mouth runner hole, the 20, the 3rd oblique hole, the 21, damping hole, the 22, the 3rd controls chamber, 23,
Second chamber, the 24, the 5th oblique hole, 25, sprue hole, 26, second section opening, 27, block button hole,
28, the second dowel hole, 29, first throttle through hole, the 30, first dowel hole.
Detailed description of the invention
In order to make the object, technical solutions and advantages of the present invention clearer, below in conjunction with accompanying drawing pair
The exemplary embodiment of the present invention is described in further detail.Obviously, described embodiment is only this
A part of embodiment of invention rather than all embodiments exhaustive.Based on the embodiment in the present invention, this
All other embodiments that field those of ordinary skill is obtained under not making creative work premise, all
To fall within the scope of the present invention.
In one embodiment of the invention, as it is shown in figure 1, give the structure of a kind of flow type balanced valve
Schematic diagram.In this embodiment, this flow type balanced valve mainly includes valve body 1, main valve plug 7, check valve
Core 13, guide valve grip assembly, the first elastic component 2 and the second elastic component 14.Wherein, guide valve grip assembly
The most fixedly sleeved with valve body 1.In other words, at least part of in guide valve grip assembly it is inserted into valve body
Fix in 1 and with valve body 1 and be connected.Main valve plug 7 and nonreturn valve core 13 are axially towards one another setting, and main valve plug
7 and nonreturn valve core 13 all arrange by the way of (or being slidably matched) by sliding and be connected in guide valve grip assembly.
The first chamber 4 accommodating the first elastic component 2 it is formed with between left side and the valve body 1 of main valve plug 7.Check valve
Core 13 and guide valve grip assembly are formed with the second chamber 23 installing the second elastic component 13.In non-oil-feed state
Under, main valve plug 7 and nonreturn valve core 13 are under the active force in opposite directions of the first elastic component 2 and the second elastic component 13
Mutually abut.It addition, guide valve grip assembly is provided with multiple throttling through hole, this throttling through hole is along with main valve plug
7 move left and right, flow area progressively changes, thus plays the effect of mild throttling.
In one embodiment of the invention, guide valve grip assembly mainly includes first guide pin bushing the 5, second guide pin bushing
9 and valve pocket 12.Nonreturn valve core 13 is slidably socketed in valve pocket 12, nonreturn valve core 13 and the one of valve pocket 12
Abut between end inwall and have the second elastic component 14.The right-hand member external diameter of nonreturn valve core 13 is than the nonreturn valve core connected
The shoulder external diameter of 13 is little, and the second elastic component 14 is socketed in the right-hand member of nonreturn valve core 4 and one end is connected to unidirectional
The shoulder of spool 13, the other end abut to valve pocket 12 right-hand member on the inwall that inner chamber extends.Specifically, may be used
With reference to Fig. 1.Nonreturn valve core 13 refers in being slidably fitted in valve pocket 12, the shoulder outer peripheral face of nonreturn valve core 13
Being slidably matched with the surface of internal cavity of valve pocket 12, the right-hand member outer peripheral face of nonreturn valve core 13 inwardly prolongs with valve pocket 12
The inwall anchor ring stretched is formed and is slidably matched, so that nonreturn valve core 13 can be along valve under oil liquid pressure effect
Overlap 12 inwalls to slidably reciprocate.
In one embodiment of the invention, guide valve grip assembly is fixed to be connected with valve body 1 and is referred to, valve pocket 12
Left end in the middle part of is connected by buckle 11 and valve body 1 is fixing, the left end of valve pocket 12 passes through near end to position
Pin 10 is fixing with the second guide pin bushing 9 to be connected, the first guide pin bushing 5 is fixing be connected to the second guide pin bushing 9 and valve body 1 it
Between.
As shown in Figure 4, a kind of concrete structure of valve pocket 12 is given.In the figure, the periphery of valve pocket 12
Face include two for the bulge loop being installed, be positioned at below bulge loop and be provided with the sprue hole connected with V hydraulic fluid port
25, the lower section in sprue hole 25 is provided with radially arranged multiple second section openings 26.Second throttling
The lower section of through hole 26 is provided with the groove for installing buckle 11, is provided with bayonet socket sky 27, block button hole in groove
The lower section of 27 is provided with the second dowel hole 28 installing alignment pin 10.
As it is shown in figure 5, give a kind of concrete structure of the second guide pin bushing 9.In the figure, the second guide pin bushing 9
Mainly include shoulders and insertion section.The upper end of insertion section is provided with multiple first throttle through hole 29, insertion section
Lower end is provided with the first dowel hole 30 installing alignment pin 10.
When mounted, the second dowel hole 28 of the first dowel hole 30 of the second guide pin bushing 9 and valve pocket 12
Correspondence also connects location by alignment pin 10.Multiple first throttle through holes 29 and the valve pocket 12 of the second guide pin bushing 9
The connection of multiple second section opening 26 positions one_to_one corresponding respectively be formed as multiple joints of guide valve grip assembly
Opening.As it is shown in figure 1, multiple the of multiple first throttle through holes 29 of the second guide pin bushing 9 and valve pocket 12
Two throttling through holes 26 are manhole, therefore, when main valve plug 7 moves axially to the left, by main valve plug 7
The through flow hole blocked gradually exposes, and flow area becomes larger；When main valve plug 7 moves right vertically,
Throttling through hole is gradually blocked, and flow area tapers into.
In one embodiment of the invention, be formed between the second guide pin bushing 9 and valve body 1 recessed position (or
It is referred to as annular gap), the right-hand member of the first guide pin bushing 5 is connected to this annular by the way of L-type structure is with clamping
In gap.In the left end of the first guide pin bushing 5 is connected to valve body 1 by the way of shoulder and some is to valve body
The interior cavity direction of 1 extends, so that valve body the 1, first guide pin bushing the 5, second guide pin bushing 9 and valve pocket 12 are formed
For there is no the standing part of relative displacement.The inner chamber of the first guide pin bushing 5 and the second guide pin bushing 9 is formed with receiving main valve
The groove of the second shoulder 7.2 of core 7, owing to the second shoulder 7.2 is limited, therefore by these groove two ends
Main valve plug 7 is restricted with the distance moved right to the left.Especially, move right when nonreturn valve core 13
Time, main valve plug 7 is owing to being limited by being positioned at second guide pin bushing 9 on right side, it is impossible to synchronize to follow nonreturn valve core
13 move right so that the fluid of V hydraulic fluid port from the gap between main valve plug 7 and nonreturn valve core 13 through unidirectional
The inner chamber of spool 13 flows to C hydraulic fluid port.
In one embodiment of the invention, as it is shown in figure 1, main valve plug 7 and nonreturn valve core 13 vertically
It is oppositely arranged.Nonreturn valve core 13 is provided with the internal diameter of bell and bell and is more than towards the side of main valve plug 7
End face external diameter towards the main valve plug 7 of nonreturn valve core 13 side.Under V hydraulic fluid port not oil-feed state, main valve plug
7 abut to the bell of nonreturn valve core 4 under the effect of the first elastic component 2 and form linear sealing, thus
Cut off V hydraulic fluid port and C hydraulic fluid port.
In one embodiment of the invention, main valve plug 7 mainly by back end cylindrical (being the left side in Fig. 1),
First shoulder the 7.1, first recess, the second shoulder 7.2 and front end (for the right in Fig. 1) are sequentially connected with composition.
Wherein, it is formed with the second recess, the second recess and the first guide pin bushing between middle part and second shoulder 7.2 of front end
5 and second guide pin bushing 9 connect formed second control chamber 8.Back end cylindrical connects first shoulder 7.1, the first recess
Being formed between first shoulder 7.1 and the second shoulder 7.2, the first recess and the first guide pin bushing 5 connect formation
One controls chamber 6.It is easily understood that first controls chamber 6 and the second control chamber 8 along with the shifting of main valve plug 7
Dynamic area can produce change, such as X hydraulic fluid port oil-feed, and when main valve plug 7 is moved to the left, second controls chamber 8
Area increase therewith.
In one embodiment of the invention, as it is shown in figure 1, the first guide pin bushing 5 is provided with the first oblique hole 18
Connect X hydraulic fluid port and second through X mouth runner hole 19 and control chamber 8；Second guide pin bushing 9 is provided with the second oblique hole
17, the second oblique hole 17 connects V hydraulic fluid port and the 3rd and controls chamber；On main valve plug, 7 are provided with the 3rd oblique hole 20
With the 4th oblique hole 16, the 3rd one end, oblique hole 20 controls chamber with first and communicates, the other end and the 4th oblique
The one end in hole 16 communicates, and the other end in the 4th oblique hole 16 and the 3rd controls chamber 22 and communicates.Therefore, exist
During X hydraulic fluid port oil-feed, act on after the active force in the second control chamber 8 overcomes the resistance of the first elastic component 2 and can push away
Dynamic main valve plug 7 is moved to the left.
In one embodiment of the invention, the front end of main valve plug 7 is provided with trumpet type hole, and this trumpet type hole exists
V hydraulic fluid port oil-feed promotes nonreturn valve core 13 to move right, and when V hydraulic fluid port connects with C hydraulic fluid port, can play buffering
The effect of oil liquid pressure.Connect with trumpet type hole is the first flow hole 15 being located in main valve plug 7.It addition,
Main valve plug 7 is positioned at first shoulder 7.1 and is provided with the 5th connected with first flow hole 15 with back end cylindrical junction
Oblique hole 24.Therefore, when V hydraulic fluid port oil-feed promotes nonreturn valve core 4 to move right, the fluid of V hydraulic fluid port
Trumpet type hole, first flow hole 19 and the 5th oblique hole 24 can be passed sequentially through and enter the left side of main valve plug 7,
So that C hydraulic fluid port acts on main valve plug 7 two ends and active force can be formed and cancel out each other.
In a preferred embodiment of the invention, in main valve plug 7, the aperture internal diameter in trumpet type hole is (i.e.
Porch diameter) and the equal diameters of back end cylindrical.The outside diameter d 3 of the front end of main valve plug 7 and first shoulder
The diameter d1 of 7.1 is equal.The diameter d2 of the second shoulder 7.2 is more than the diameter d1 of first shoulder 7.1.Therefore,
The fluid in the left side that C hydraulic fluid port enters main valve plug 7 acts on the active force of main valve plug 7 and acts on master with C hydraulic fluid port
The active force on the right side of spool 7 is of substantially equal, can cancel each other out.It is, the unlatching of main valve plug 7
The most not by the pressure influence of C hydraulic fluid port.It addition, the first fluid controlling chamber 6 can be directly through V hydraulic fluid port stream
Go out.Therefore, the unlatching of main valve plug is only relevant with the pretightning force controlling pressure and the first elastic component 2 of X hydraulic fluid port.
As in figure 2 it is shown, give the principle schematic of the flow type balanced valve of the present invention.According to this figure, this
The operation principle of the flow type balanced valve of the present invention is: when V hydraulic fluid port oil-feed, and nonreturn valve core 13 is opened,
Play the effect of quick oil feeding.When X hydraulic fluid port oil-feed, main valve plug 7 is opened, and along with the shifting of main valve plug 7
Dynamic, it is turned on and off the throttling through hole on part or all of guide valve grip assembly, thus plays mild throttling
Effect.
As it is shown on figure 3, give the principle signal of a kind of hydraulic circuit using inventive flow type balanced valve
Figure.In the figure, the A mouth of reversal valve connects the V hydraulic fluid port of inventive flow type balanced valve, stream of the present invention
The C hydraulic fluid port of amount type balanced valve connects hydraulic cylinder rodless cavity, the oil of the X hydraulic fluid port of inventive flow type balanced valve
Hydraulic coupling by operating handle control,.This hydraulic circuit operationally, including rise, stop and declining this three
Individual process, specific works process is as follows:
(1) uphill process.The pressure oil of reversal valve arrives the V hydraulic fluid port of flow type balanced valve, V hydraulic fluid port
Pressure oil overcomes the pretightning force of the second elastic component 14 to promote nonreturn valve core 13 to move right unlatching, pressure oil warp
V hydraulic fluid port flows into C hydraulic fluid port and arrives hydraulic cylinder rodless cavity, promotes hydraulic cylinder up.This stage fluid is by V mouth
Flow into C mouth and there is no throttling action.
(2) process is declined.The pressure oil of X hydraulic fluid port enters the second control chamber 8 and is applied on main valve plug 7,
Overcome the pretightning force of the first elastic component 2, make main valve plug 7 move to left.Nonreturn valve core 13 is against the second guide pin bushing 9
Right-hand member cut off V hydraulic fluid port and C hydraulic fluid port.When X hydraulic fluid port pressure increases, main valve plug 7 moves to left further,
The second guide pin bushing 9 covered in by main valve plug 7 diameter before progressively exposing and each joint communicated on valve pocket 12
Opening so that area of passage relaxes to be increased, load lowering velocity can be precisely controlled.And because not
Need as prior art, on main valve plug 7, open a lot of grooves, decrease a lot of processing technique, be processed into
This reduction, and the rigidity of main valve plug 7 will not be had any impact.
(3) stopped process.X hydraulic fluid port pressure reduces, and the first elastic component 2 promotes main valve plug 7 to move to right, mistake
Flow area is gradually reduced, until being shut by the valve port of main valve plug 7.
Although preferred embodiments of the present invention have been described, but those skilled in the art once know base
This creativeness concept, then can make other change and amendment to these embodiments.So, appended right is wanted
Ask and be intended to be construed to include preferred embodiment and fall into all changes and the amendment of the scope of the invention.Additionally may be used
To be understood by, as long as the conflict not existed in structure, the feature in each embodiment all can be combined with each other,
The combination type feature formed still falls within the scope of the present invention.The invention is not limited in spy disclosed herein
Determine embodiment, but include all technical schemes fallen within the scope of the appended claims.
Claims (9)
1. a flow type balanced valve, it is characterised in that include valve body, main valve plug, nonreturn valve core, lead
To valve pocket assembly, the first elastic component and the second elastic component, described guide valve grip assembly and valve body fixed cover in opposite directions
Connecing, described main valve plug and nonreturn valve core are axially towards one another and are slidably arranged in described guide valve grip assembly, described
First elastic component is located between valve body and main valve plug, and described second elastic component is located at guide valve grip assembly with unidirectional
Between spool；Described main valve plug and described guide valve grip assembly sequentially form the first control chamber and the X of valve body
The second of hydraulic fluid port connection controls chamber and the 3rd control chamber connected with the V hydraulic fluid port of valve body；Described first controls chamber
Control chamber with the 3rd to be connected by the runner hole on main valve plug；Described guide valve grip assembly is formed radially
V hydraulic fluid port and axial C hydraulic fluid port, described V hydraulic fluid port is positioned at the junction of main valve plug and nonreturn valve core, described C
Arrange in the inner chamber of hydraulic fluid port and described nonreturn valve core and main valve plug fluid course connect；Described guide valve
Grip assembly is radially provided with multiple throttling through hole near V hydraulic fluid port；When V hydraulic fluid port oil-feed, nonreturn valve core is opened,
V hydraulic fluid port connects with C hydraulic fluid port；Promote main valve plug vertically to compressing the first elastic component when X hydraulic fluid port oil-feed
When direction is moved, the throttling through hole of guide valve grip assembly progressively exposes.
2. flow type balanced valve as claimed in claim 1, it is characterised in that described guide valve grip assembly
Including the first guide pin bushing, the second guide pin bushing and valve pocket, described nonreturn valve core is located in one end of described valve pocket, described
Snapping connection with valve body in the middle part of the other end of valve pocket, the other end of described valve pocket leads to the second guide pin bushing near end
Cross alignment pin to connect, between described second guide pin bushing and described valve body, be formed with recessed position, described first guide pin bushing
It is connected to described recessed position and some extends to described body cavity direction.
3. flow type balanced valve as claimed in claim 2, it is characterised in that described second guide pin bushing includes
Shoulders and insertion section, the front end edge of described insertion section is radially provided with multiple first throttle through hole, described insertion
The rear end in portion is provided with the first dowel hole, and described valve pocket is radially provided with the multiple first throttles with insertion section
Multiple second section openings of through hole one_to_one corresponding connection and the corresponding with the first dowel hole second location
Pin-and-hole.
4. flow type balanced valve as claimed in claim 3, it is characterised in that the plurality of first throttle
On the periphery of the front end, insertion section that through hole is evenly distributed on described second guide pin bushing so that main valve plug is to compression the
When the direction of one elastic component is moved, first throttle through hole and corresponding second section opening connect with C hydraulic fluid port
Area of passage incrementally increases.
5. the flow type balanced valve as according to any one of claim 2 to 4, it is characterised in that described
First guide pin bushing is provided with the first oblique hole, and described first oblique hole connection X hydraulic fluid port and second controls chamber；Described
Second guide pin bushing is provided with the second oblique hole, and described second oblique hole connection V hydraulic fluid port and the 3rd controls chamber；Described
Main valve plug is provided with the 3rd oblique hole and the 4th oblique hole, and described 3rd one end, oblique hole controls chamber phase with first
Logical, the other end communicates with the one end in described 4th oblique hole, the other end in described 4th oblique hole and the 3rd control
Chamber processed communicates.
6. flow type balanced valve as claimed in claim 1, it is characterised in that described nonreturn valve core towards
The side of main valve plug is provided with the internal diameter of bell and described bell more than the main valve plug towards nonreturn valve core side
End face external diameter, under V hydraulic fluid port not oil-feed state, described main valve plug abuts under the effect of the first elastic component
The bell of described nonreturn valve core also forms linear sealing and cuts off V hydraulic fluid port and C hydraulic fluid port.
7. flow type balanced valve as claimed in claim 1, it is characterised in that described main valve plug includes depending on
The back end cylindrical of secondary connection, first shoulder, the first recess, the second shoulder and front end, front end is near second
Being formed with the second recess at shoulder, described second to control chamber be described second recess and the first guide pin bushing and the second guide pin bushing
Connect and formed；Described first recess connects first shoulder and the second shoulder, and described first recess and first is led
Set connects formation the first control chamber；Have the 3rd recess in the middle part of described main valve plug leading portion, and described 3rd recess with
First valve pocket connects formation the 3rd control chamber.
8. flow type balanced valve as claimed in claim 7, it is characterised in that described main valve plug is towards institute
The one end stating nonreturn valve core is provided with axial trumpet type hole, and described main valve plug is additionally provided with one end and trumpet type
The first flow hole of hole connection and the 5th oblique hole that connects with the other end in first flow hole, the described 5th
The other end in oblique hole is positioned at first shoulder and the back end cylindrical junction of described main valve plug.
9. flow type balanced valve as claimed in claim 8, it is characterised in that the hole in described trumpet type hole
Mouth internal diameter and the equal diameters of back end cylindrical, the diameter of described main valve plug front end is equal to the diameter of first shoulder,
The diameter of described second shoulder is more than the diameter of first shoulder.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201610578641.4A CN105971965B (en) | 2016-07-19 | 2016-07-19 | Flow type balanced valve |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610578641.4A CN105971965B (en) | 2016-07-19 | 2016-07-19 | Flow type balanced valve |
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| CN105971965A true CN105971965A (en) | 2016-09-28 |
| CN105971965B CN105971965B (en) | 2017-12-19 |
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| CN201610578641.4A Expired - Fee Related CN105971965B (en) | 2016-07-19 | 2016-07-19 | Flow type balanced valve |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108061069A (en) * | 2017-12-19 | 2018-05-22 | 宁波文泽机电技术开发有限公司 | Buffer overflow valve |
| CN108930681A (en) * | 2018-08-21 | 2018-12-04 | 东莞海特帕沃液压科技有限公司 | A kind of balanced valve of Discrete control |
| CN108953713A (en) * | 2018-08-22 | 2018-12-07 | 东莞海特帕沃液压科技有限公司 | Flow type balanced valve |
| CN109058199A (en) * | 2018-08-20 | 2018-12-21 | 宁波汉商液压有限公司 | A kind of stall proof clearance-type super-pressure relief valve |
| CN110762069A (en) * | 2018-07-27 | 2020-02-07 | 比亚迪股份有限公司 | Hydraulic control system |
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| CN108061069A (en) * | 2017-12-19 | 2018-05-22 | 宁波文泽机电技术开发有限公司 | Buffer overflow valve |
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| CN109058199A (en) * | 2018-08-20 | 2018-12-21 | 宁波汉商液压有限公司 | A kind of stall proof clearance-type super-pressure relief valve |
| CN108930681A (en) * | 2018-08-21 | 2018-12-04 | 东莞海特帕沃液压科技有限公司 | A kind of balanced valve of Discrete control |
| CN108953713A (en) * | 2018-08-22 | 2018-12-07 | 东莞海特帕沃液压科技有限公司 | Flow type balanced valve |
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| Publication number | Publication date |
|---|---|
| CN105971965B (en) | 2017-12-19 |
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Effective date of registration: 20171012 Address after: Shuanghu Road high-tech economic zone 224005 Jiangsu province Yancheng City Jianhu County No. 998 Applicant after: JIANGSU YUANDA MACHINERY TECHNOLOGY Co.,Ltd. Address before: 315000 Zhejiang province Ningbo city Ningbo high tech Zone Juxian Road No. 555 building 035 room 18-1 No. 013 station Applicant before: NINGBO WENZE ELECTROMECHANICAL TECHNOLOGY DEVELOPMENT Co.,Ltd. |
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