CN106015152B - Slowly the flow type balanced valve closed is changed up - Google Patents
Slowly the flow type balanced valve closed is changed up Download PDFInfo
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- CN106015152B CN106015152B CN201610574689.8A CN201610574689A CN106015152B CN 106015152 B CN106015152 B CN 106015152B CN 201610574689 A CN201610574689 A CN 201610574689A CN 106015152 B CN106015152 B CN 106015152B
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- hydraulic fluid
- fluid ports
- hole
- main valve
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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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
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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
- 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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0407—Means for damping the valve member movement
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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
- F16K17/20—Excess-flow valves
- F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
- F16K17/24—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member
- F16K17/28—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only
- F16K17/30—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only spring-loaded
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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
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/22—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution
- F16K3/24—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members
- F16K3/26—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members with fluid passages in 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
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/30—Details
- F16K3/316—Guiding of the slide
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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
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/30—Details
- F16K3/32—Means for additional adjustment of the rate of flow
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Safety Valves (AREA)
Abstract
The invention discloses a kind of flow type balanced valve for changing up close slowly, including valve body, main valve plug, nonreturn valve core, guide valve set component, damping check valve, the first elastic component and the second elastic component, the guide valve set component and valve body are fixedly sleeved in opposite directions, the main valve plug and nonreturn valve core, which are axially towards one another, to be slidably arranged in the guide valve set component, the valve body is provided with Y hydraulic fluid ports and X hydraulic fluid ports, the guide valve set component forms V hydraulic fluid ports and C hydraulic fluid ports, and the C hydraulic fluid ports connect with the fluid course set in the inner chamber of the nonreturn valve core and main valve plug；The guide valve set component is provided with multiple throttling through holes vertically close to V hydraulic fluid ports；In V hydraulic fluid port oil-feeds, nonreturn valve core is opened, and V hydraulic fluid ports connect with C hydraulic fluid ports；Promote main valve plug vertically to the movement of the first elastic component direction of compression in X hydraulic fluid port oil-feeds, main valve plug is damped the damping action of check valve, and the throttling through hole of guide valve set component exposes, and flow area incrementally increases.This changes up the control load lowering velocity that the flow type balanced valve processing closed is simpler, excessively stream is gentler, can be precise and stable slowly, using reliable.
Description
Technical field
The present invention relates to control valve technical field, more particularly to a kind of control load lowering velocity that can be accurate and stable
Slow change up the flow type balanced valve closed.
Background technology
In the plant equipment such as modern engineering machinery, building machinery, raising hydraulic circuit, wherein balanced valve have been widely applied
It is to control the crucial Hydraulic Elements that hydraulic jack works in hoisting circuit, the quality for balancing valve performance directly affects the property of main frame
Energy.Existing such a shortcoming of hydraulically balanced valve generally existing：When loading decentralization, due to hydraulically balanced valve valve port flow-passing surface
Product can produce the characteristics of mutation, and load can be made to produce low-frequency jitter and the phenomenon of impact, cause system unstable, influence complete machine
Security reliability.
Patent announcement number is CN103470815B, the patent of invention of entitled " balanced valve " provides a kind of flow-passing surface gradually
The balanced valve of change, it is combined by milling out groove, aperture and inclined hole that multiple width differ on poppet valve core, reaches flow gradual change
Purpose.But this design has the following disadvantages：
(1) what is passed through when load decentralization and load rise is same valve port, can all produce restriction effect, and is loaded in practice
It is not need throttling action during rising, has a strong impact on the efficiency of operation；A check valve in parallel, nothing are also needed in order to solve this problem
Expense is added in shape；
(2) after groove is milled out on poppet valve core and drills out aperture and inclined hole, the rigidity of valve element substantially reduces, in the case where control loads
Larger pressure difference and quick liquid flow impact are born when putting, be heat-treated in addition it is bad if, valve element is easy to break, and reliability is big
It is big to reduce；
(3) groove milling on poppet valve core, processed complex, efficiency are low, therefore cost of manufacture is high；
(4) unlatching of valve element is influenceed by load with return oil pressure, when load is very big and return oil pressure is small, it is only necessary to very
Small control pressure can allows valve port to reach very big position, can also produce flow mutation.
(5) when control pressure produces impact, valve element can be promoted quickly to move, although valve element is provided with throttling channel,
It can cause to shake so as to produce flow mutation greatly because the quick movement of valve element causes area of passage moment to become.By in control mouth
Damping hole is set, though valve element opening speed can be slowed down, speed when valve element is closed can be equally reduced, be glided when causing load to stop
Apart from excessive.
The content of the invention
The defects of it is an object of the invention to overcome prior art, there is provided it is a kind of to change up the flow type balanced valve closed slowly, should
Balanced valve processing is simpler, excessively stream is gentler, can accurately control load lowering velocity and realizing to change up slowly closes, using can
Lean on.
For above technical problem, technical solution of the invention is to provide a kind of changing up slowly with following structure
The flow type balanced valve closed, the balanced valve include：Valve body, main valve plug, nonreturn valve core, guide valve set component, one-way damper valve, the
One elastic component and the second elastic component, guide valve set component and valve body are fixedly sleeved in opposite directions, main valve plug and nonreturn valve core phase vertically
To being slidably arranged in guide valve set component, the first elastic component is located between valve body and main valve plug, and the second elastic component is located at guiding
Between valve pocket component and nonreturn valve core；Main valve plug sequentially forms the connected with the Y hydraulic fluid ports of valve body first control with guide valve set component
The C oil of chamber processed and the V hydraulic fluid port and axial direction of the second control chamber guide valve set component formed with radial direction that are connected with the X hydraulic fluid ports of valve body
Mouthful, V hydraulic fluid ports are located at the junction of main valve plug and nonreturn valve core, are set in the inner chamber and main valve plug of C hydraulic fluid ports and nonreturn valve core
Fluid course connection；One end slip cap of the main valve plug away from C hydraulic fluid ports is connected to one-way damper valve；Guide valve set component is close
V hydraulic fluid ports are provided with multiple throttling through holes vertically；In V hydraulic fluid port oil-feeds, nonreturn valve core is opened, and V hydraulic fluid ports connect with C hydraulic fluid ports；In X oil
Promote main valve plug vertically to during the movement of the first elastic component direction of compression during mouth oil-feed, the throttling through hole of guide valve set component is progressively
Expose, damping hole of the fluid of chamber through the one-way damper valve where first elastic component flows to C hydraulic fluid ports, now unidirectional resistance
Buddhist nun's valve plays damping action, slows down the speed of main valve plug unlatching.
In the non-oil-feed of V hydraulic fluid ports, main valve plug is with nonreturn valve core in the first elastic component and the opposite active force of the second elastic component
It is lower to close so as to separate V hydraulic fluid ports and C hydraulic fluid ports.In V hydraulic fluid port oil-feeds, nonreturn valve core is opened, and V hydraulic fluid ports connect with C hydraulic fluid ports.In X hydraulic fluid ports
Promote main valve plug vertically to during the movement of the first elastic component direction of compression during oil-feed, the throttling through hole of guide valve set component exposes,
Flow area incrementally increases.Herein, guide valve set component and valve body are opposite fixedly sleeved refers to guide valve set component at least portion
Divide in insertion valve body and form a fixed connection.Main valve plug and nonreturn valve core, which are axially towards one another, to be slidably arranged in guide valve set component
Refer to, main valve plug and the axially opposed setting of nonreturn valve core, and guide valve set component is located at by way of being slidably matched.
Further, guide valve set component is mainly located at valve pocket including the first guide pin bushing, the second guide pin bushing and valve pocket, nonreturn valve core
One end in, snapped connection in the middle part of the other end of valve pocket with valve body, the other end of valve pocket passes through calmly close to end and the second guide pin bushing
Position pin connection, formed with recessed position between the second guide pin bushing and valve body, the first guide pin bushing be connected to recessed position and some to
Body cavity direction extends.It is understood that the first elastic component is located in the first chamber that valve body is formed with valve element, first leads
One end of set extends to valve inner or inner chamber (namely first chamber direction), and therefore, the first elastic component is to nonreturn valve core side
To motion limited by the first guide pin bushing to valve extension position and the main valve plug distance that moves right.In addition, the present invention's
In one scheme, multiple throttling through holes are distributed in the position between V hydraulic fluid ports 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 holes, inserts
The rear end for entering portion is provided with the first dowel hole, and valve pocket is provided with corresponds what is connected with multiple first throttle through holes of insertion section
Multiple second throttling through holes and the second dowel hole corresponding with the first dowel hole.
In a preferred embodiment, the diameter of first throttle through hole respectively with corresponding second throttling through-hole diameter phase
Deng.Because first throttle through hole and the second throttling through hole are to correspond, therefore when not blocked, the section after the connection of formation
The area of passage of opening is exactly the area of corresponding first throttle through hole or the second throttling through hole.
In one embodiment, multiple first throttle through holes are evenly distributed on the different rings of the insertion section front end of the second guide pin bushing
Arranged on shape section and along the front end side face of insertion section so that when the direction of main valve plug to the first elastic component of compression is moved increasingly
More first throttle through holes and corresponding second throttling through hole connect with C hydraulic fluid ports.Be advantageous to precisely control the decline of load
Speed, work are more reliable.
In one embodiment, the first guide pin bushing is provided with the first oblique hole and the second oblique hole, the first oblique hole connection Y oil
Mouth and the first control chamber, the second oblique hole connection X hydraulic fluid ports and the second control chamber.
Further, nonreturn valve core is provided with the internal diameter of conical opening and conical opening more than towards unidirectionally towards the side of main valve plug
The main valve plug end face external diameter of valve element side, in the case where V hydraulic fluid ports do not enter oil condition, main valve plug abuts to list in the presence of the first elastic component
Conical opening to valve element simultaneously forms linear sealing and separates V hydraulic fluid ports and C hydraulic fluid ports.
Further, main valve plug includes back end cylindrical, first shoulder, the first recess, the second shoulder and preceding being sequentially connected
End, formed with the second recess at the second shoulder, the second control chamber is the second recess and the first guide pin bushing and the second guide pin bushing for front end
Connection is formed；First recess connects first shoulder and the second shoulder, and the first recess is connected to form the first control with the first guide pin bushing
Chamber.
Preferably, main valve plug is provided with the loudspeaker type hole of axial direction towards one end of nonreturn valve core, and one is additionally provided with main valve plug
The first flow hole connected with loudspeaker type hole and the 3rd oblique hole connected with the other end in first flow hole are held, the 3rd is oblique
The other end in hole is located at first shoulder and the back end cylindrical junction of main valve plug.
In a preferred embodiment, the aperture internal diameter of loudspeaker type hole is equal with the diameter of back end cylindrical, outside front end
Footpath is equal with the diameter of first shoulder, and the diameter of the second shoulder is more than the diameter of first shoulder.
Further, spring base and steel ball are provided between the first elastic component and the back end cylindrical of main valve plug.
Preferably, one-way damper valve is actively socketed on back end cylindrical, the side face where one-way damper valve maximum gauge with
Liquid stream space be present between the corresponding position of guide valve set component, when main valve plug moves to nonreturn valve core direction, the oil of C hydraulic fluid ports
Liquid is through the liquid stream space with being located at the first elastic component place chamber.Therefore, when main valve plug moves toward the direction closed,
The pressure top opening one-way orifice valve of C hydraulic fluid ports, the fluid of C hydraulic fluid ports are covered between component and one-way damper valve and main valve plug through guide valve
Space flow to chamber where the first elastic component, now one-way damper valve does not play damping action, and main valve plug realizes quick closedown.
Beneficial effects of the present invention are as follows：
The flow type balanced valve of the present invention in a valve body by setting a nonreturn valve core and one to be used for what is throttled
Main valve plug, and by way of covering and throttling through hole is set on component in guide valve, the movement of control bound core just can be more accurate
Ground controls area of passage so that is not limited when hydraulic cylinder rises by throttling, when hydraulic cylinder declines by than shallower section
Flow control.Flow type balanced valve in the present invention is recessed due to that need not process many as balanced valve of the prior art
Groove, overall processing is simpler, and excessively stream is gentler, can accurately control load lowering velocity, and use is more reliable.
Secondly, the fluid course in main valve plug is set, and the fluid of C hydraulic fluid ports is incorporated into the opposite side of main valve plug so that C oil
Mouthful the active force that acts on main valve plug both ends of pressure can mutually balance so that the unlatching of main valve plug substantially not by
Load effect.In addition, the fluid of the first control chamber directly can outflow back to fuel tank through Y hydraulic fluid ports, do not connected with V hydraulic fluid ports, it is therefore, main
The unlatching of valve element is not also influenceed by V hydraulic fluid port pressure, only relevant with the control pressure of X hydraulic fluid ports and the pretightning force of the first elastic component.
In addition, one-way damper valve is set between the first flexible member chamber and C mouths so that main valve plug is hindered when opening
Buddhist nun acts on and opened slowly, effect quick closedown not dampened when main valve plug is closed, realizes the buffering to X mouth compression shocks, to negative
It is more stable to carry speed control, sinks when load stops apart from small.
Brief description of the drawings
Technical scheme in order to illustrate the embodiments of the present invention more clearly, make required in being described below to embodiment
Accompanying drawing is briefly introduced.It should be evident that drawings discussed below is only some embodiments of the present invention, for ability
For the those of ordinary skill in domain, on the premise of not paying creative work, it can also be obtained according to these accompanying drawings other
Accompanying drawing.
Fig. 1 show the slow structural representation for changing up the flow type balanced valve one of which embodiment closed of the present invention；
Fig. 2 show the slow principle schematic for changing up the flow type balanced valve closed in Fig. 1；
Fig. 3 show the principle schematic using the slow hydraulic circuit for changing up the flow type balanced valve closed of the present invention；
Fig. 4 show a kind of structural representation of the valve pocket in Fig. 1；
Fig. 5 show a kind of structural representation of the second guide pin bushing in Fig. 1；
Fig. 6 is a kind of structural representation of the one-way damper valve in Fig. 1.
In figure：1st, valve body, the 2, first elastic component, 3, spring base, 4, nonreturn valve core, the 5, first guide pin bushing, the 6, first control chamber,
7th, main valve plug, 7.1, first shoulder, the 7.2, second shoulder, the 8, second control chamber, the 9, second guide pin bushing, 10, alignment pin, 11, buckle,
12nd, valve pocket, the 13, second elastic component, 14, second flow channel hole, the 15, second oblique hole, 16, X mouth runners hole, 17, Y mouth runners hole,
18th, the first oblique hole, 19, first flow hole, the 20, second dowel hole, 21, block button hole, the 22, second throttling through hole, 23, main flow
Road hole, the 24, first dowel hole, 25, first throttle through hole, 26, steel ball, the 27, the 3rd oblique hole, 28, one-way damper valve, 29,
Damping hole.
Embodiment
In order that the object, technical solutions and advantages of the present invention are more clearly understood, below in conjunction with accompanying drawing to the present invention
Exemplary embodiment be described in further detail.Obviously, described embodiment is only the part implementation of the present invention
Example, rather than the exhaustion of all embodiments.Based on the embodiment in the present invention, those of ordinary skill in the art are not making wound
The all other embodiment obtained under the premise of the property made work, falls within the scope of protection of the invention.
In one embodiment of the invention, as shown in figure 1, giving a kind of slow knot for changing up the flow type balanced valve closed
Structure schematic diagram.In this embodiment, this changes up the flow type balanced valve closed slowly mainly includes valve body 1, main valve plug 7, nonreturn valve core
4th, guide valve set component, one-way damper valve 28, the first elastic component 2 and the second elastic component 13.Wherein, guide valve set component and valve body
1 is opposite fixedly sleeved.In other words, it is at least part of in guide valve set component to be inserted into valve body 1 and fix company with valve body 1
Connect.Main valve plug 7 and nonreturn valve core 4 are axially towards one another setting, and main valve plug 7 and nonreturn valve core 4 are set by sliding and (or slided
Coordinate) mode be connected to guide valve set component in.Formed with the first elastic component 2 of receiving between the left side of main valve plug 7 and valve body 1
First chamber.Nonreturn valve core 4 and second chamber of the guide valve set component formed with the second elastic component 13 of installation.Do not entering oily
Under state, main valve plug 7 and nonreturn valve core 4 mutually abut in the first elastic component 2 with the opposite active force of the second elastic component 13.Separately
Outside, guide valve set component is provided with multiple throttling through holes, throttling through hole the moving left and right with main valve plug 7, flow area by
Step changes, so as to play a part of gently throttling.In addition, when main valve plug 7 is moved to the left unlatching, one-way damper valve 28 is sent out
Wave damping action.
In one embodiment of the invention, guide valve set component mainly includes the first guide pin bushing 5, the second guide pin bushing 9 and valve pocket
12.Nonreturn valve core 4 is slidably socketed in valve pocket 12, and the second elasticity has been abutted between nonreturn valve core 4 and one end inwall of valve pocket 12
Part 13.The right-hand member external diameter of nonreturn valve core 4 is smaller than the shoulder external diameter of the nonreturn valve core 4 of connection, and the second elastic component 13 is socketed in unidirectionally
The right-hand member of valve element 4 and one end are connected to the shoulder of nonreturn valve core 4, the other end abuts to the inwall that the right-hand member of valve pocket 12 extends to inner chamber
On.Specifically, it can refer to Fig. 1.Nonreturn valve core 4, which is slidably fitted in valve pocket 12, to be referred to, the shoulder outer peripheral face and valve of nonreturn valve core 4
The surface of internal cavity of set 12 is slidably matched, and the inwall anchor ring that right-hand member outer peripheral face and the valve pocket 12 of nonreturn valve core 4 extend internally forms cunning
It is dynamic to coordinate, so that nonreturn valve core 4 can slidably reciprocate along the inwall of valve pocket 12 under oil liquid pressure effect.
In one embodiment of the invention, guide valve set component is fixedly connected with valve body 1 refers to, in the left end of valve pocket 12
Portion is fixedly connected by buckle 11 with valve body 1, and the left end of valve pocket 12 is fixed close to end by the guide pin bushing 9 of alignment pin 10 and second to be connected
Connect, the first guide pin bushing 5 is fixed and is connected between the second guide pin bushing 9 and valve body 1.
As shown in figure 4, give a kind of concrete structure of valve pocket 12.In the figure, the outer peripheral face of valve pocket 12 includes two
The individual bulge loop for being loaded, is provided with the sprue hole 23 connected with V hydraulic fluid ports below bulge loop, and the lower section in sprue hole 23 is set
There are multiple second throttling through holes 22 along side face arrangement.Section where the axis of multiple second throttling through holes 22 is gradually distance from main flow
The place section of road hole 23.The lower section of second throttling through hole 22, which is provided with, is used to installing the block button hole 21 of buckle 11, under block button hole 21
Side is provided with the second dowel hole 20 of installation alignment pin 10.
As 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 includes platform
Shoulder and insertion section.The upper end of insertion section is provided with multiple first throttle through holes 25, and the lower end of insertion section is provided with installation alignment pin 10
The first dowel hole 24.
When mounted, the second dowel hole 20 of the first dowel hole 24 of the second guide pin bushing 9 and valve pocket 12 is corresponding and passes through
The connection positioning of alignment pin 10.Multiple second throttling through holes 22 of multiple first throttle through holes 25 of second guide pin bushing 9 and valve pocket 12
Put and correspond multiple throttling through holes that connection is formed as guide valve set component respectively.As shown in figure 1, due to the second guide pin bushing 9
Multiple second throttlings through holes 22 of multiple first throttle through holes 25 and valve pocket 12 are not on same section, but axially
Distribution, therefore, when main valve plug 7 moves axially to the left, is gradually exposed, flow area by the throttling through hole that main valve plug 7 blocks
Become 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, between the second guide pin bushing 9 and valve body 1 formed with recessed position (or for annular
Gap), the right-hand member of the first guide pin bushing 5 is connected in the annular gap L-type structure in a manner of clamping.A left side for first guide pin bushing 5
End is connected to by way of shoulder in valve body 1 and some extends to the interior cavity direction of valve body 1, so that valve body 1, the
One guide pin bushing 5, the second guide pin bushing 9 and valve pocket 12 are formed without the fixed part of relative displacement.First guide pin bushing 5 and the second guide pin bushing 9
Groove of the inner chamber formed with the second shoulder 7.2 for accommodating main valve plug 7, because the second shoulder 7.2 is limited by the groove both ends,
Therefore main valve plug 7 is restricted with the distance to move right to the left.Especially, when nonreturn valve core 4 moves right, main valve plug 7
Due to being limited by the second guide pin bushing 9 positioned at right side, it is impossible to synchronously follow nonreturn valve core 4 to move right, obtain the fluid of V hydraulic fluid ports
Inner chamber of the gap through nonreturn valve core 4 between main valve plug 7 and nonreturn valve core 4 flows to C hydraulic fluid ports.
In one embodiment of the invention, as shown in figure 1, main valve plug 7 and nonreturn valve core 4 are axially towards one another setting.It is single
The internal diameter of conical opening and conical opening is provided with more than the main valve plug 7 towards the side of nonreturn valve core 4 to valve element 4 towards the side of main valve plug 7
End face external diameter.In the case where V hydraulic fluid ports do not enter oil condition, main valve plug 7 abuts to nonreturn valve core 4 in the presence of the first elastic component 2
Conical opening simultaneously forms linear sealing, so as to separate V hydraulic fluid ports and C hydraulic fluid ports.
In one embodiment of the invention, main valve plug 7 is mainly by back end cylindrical (being the left side in Fig. 1), first shoulder
7.1st, the first recess, the second shoulder 7.2 and front end (being the right in Fig. 1) are sequentially connected composition.Wherein, the middle part of front end and second
Formed with the second recess between shoulder 7.2, the second recess is connected with the first guide pin bushing 5 and the second guide pin bushing 9 forms the second control chamber 8.
Back end cylindrical connect first shoulder 7.1, the first recess formed between the shoulder 7.2 of first shoulder 7.1 and second, the first recess with
The connection of first guide pin bushing 5 forms the first control chamber 6.It is easily understood that the first control chamber 6 and the second control chamber 8 are with main valve plug 7
Migration area can produce change, such as X hydraulic fluid port oil-feeds, when main valve plug 7 is moved to the left, the area of the second control chamber 8 increases therewith
Greatly.
In one embodiment of the invention, as shown in figure 1, the first guide pin bushing 5 is oblique provided with the first oblique hole 18 and second
To hole 15.Y hydraulic fluid ports are corresponded on valve body 1 and are provided with Y mouth runners hole 17, corresponding X hydraulic fluid ports are provided with X mouth runners hole 16.First oblique hole 18
Y hydraulic fluid ports and the first control chamber are connected through Y mouth runners hole 17.Second oblique hole 15 connects X hydraulic fluid ports and the second control through X mouth runners hole 16
Chamber processed.Therefore, in X hydraulic fluid port oil-feeds, act on the second control chamber active force overcome the resistance of the first elastic component 2 after can promote
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 loudspeaker type hole, and the loudspeaker type hole is entered in V hydraulic fluid ports
Oil promotes nonreturn valve core 4 to move right, and when V hydraulic fluid ports connect with C hydraulic fluid ports, can play a part of buffering oil liquid pressure.With trumpet type
Hole connection is the first flow hole 19 being located in main valve plug 7.Connect in addition, main valve plug 7 is located at first shoulder 7.1 with back end cylindrical
Meet place and be provided with the 3rd oblique hole 27 connected with first flow hole 19.Therefore, nonreturn valve core 4 is promoted to move right in the oil-feed of V hydraulic fluid ports
When dynamic, the fluid of V hydraulic fluid ports can pass sequentially through loudspeaker type hole, a left side for the oblique hole 27 of first flow hole 19 and the 3rd entrance main valve plug 7
Side, so that C hydraulic fluid ports act on the both ends of main valve plug 7 and can be formed and cancelled out each other.
In a preferred embodiment of the invention, in main valve plug 7, (i.e. porch is straight for the aperture internal diameter of loudspeaker type hole
Footpath) it is equal with the diameter of back end cylindrical.The outside diameter d 2 of the front end of main valve plug 7 is equal with the diameter d1 of first shoulder 7.1.Second
The diameter d3 of shoulder 7.2 is more than the diameter d1 of first shoulder 7.1.Therefore, C hydraulic fluid ports act on into the fluid in the left side of main valve plug 7
The active force on the right side that the active force of main valve plug 7 acts on main valve plug 7 with C hydraulic fluid ports is of substantially equal, can cancel each other out.Also
It is that the unlatching of main valve plug 7 is not substantially by the pressure influence of C hydraulic fluid ports.In addition, the fluid of the first control chamber 6 can be directly through Y hydraulic fluid port streams
Go out and return to fuel tank, do not connected with V hydraulic fluid ports, therefore, the unlatching of main valve plug is not also influenceed by V hydraulic fluid port pressure, only the control with X hydraulic fluid ports
The pretightning force of pressing pressure and the first elastic component 2 is relevant.
In addition, in order that the active force between main valve plug 7 and the first elastic component 2 is more balanced, the elastic component of main valve plug 7 and first
Spring base 3 and steel ball 26 are additionally provided between 2.First elastic component 2 is socketed on the left side round platform of spring base 3, and the first elastic component 2
Side abut the inwall of valve body 1, the opposite side of the first elastic component 2 abuts spring base 3.Tied formed with buffering on the right side of spring base 3
Structure, right side central are provided with the groove for accommodating steel ball 26.Spring base 3 is connected by steel ball 26 with the back end cylindrical of main valve plug 7.
In one embodiment of the invention, one-way damper valve 28 is actively socketed on the back end cylindrical of main valve plug 7, unidirectionally
Liquid stream space be present between covering the corresponding position of component in side face and guide valve where the maximum gauge of orifice valve 28, in other words,
Internal diameter of the one-way damper valve maximum gauge of one-way damper valve 28 much smaller than the corresponding position of guide valve set component.When main valve plug 7
When being moved towards the direction (direction that in Fig. 1 to the left, i.e., main valve plug 7 is opened) of the first elastic component 2 of compression, one-way damper valve 28
Big end abuts in the left side of first shoulder 7.1 of main valve plug 7, damping hole 29 and the fluid course in main valve plug 7 of one-way damper valve
Connection, plays damping action.When main valve plug 7 towards nonreturn valve core 4 direction (in Fig. 1 to the right, i.e., main valve plug 7 close direction)
When mobile, the pressure of C hydraulic fluid ports is acted on one-way damper valve by the fluid course in main valve plug 7 and makes one-way damper valve relative
First shoulder 7.1 is moved to the left, and now liquid stream is successively through the fluid course in C hydraulic fluid ports, main valve plug 7, one-way damper valve 28 and master
Space between valve element 7 flows to the first flexible member chamber, and now one-way damper valve does not have damping action.It is it is, unidirectional
Orifice valve plays damping action in the direction that main valve plug 7 is opened, and damping can not be fully opened in the direction that main valve plug 7 is closed and is made
With.
As shown in Fig. 2 give the slow principle schematic for changing up the flow type balanced valve closed of the present invention.According to the figure,
This present invention it is slow change up the flow type balanced valve closed operation principle be：When V hydraulic fluid port oil-feeds, nonreturn valve core 4 is opened, and is played
The effect of quick oil feeding.When X hydraulic fluid port oil-feeds, main valve plug 7 is opened, and with the movement of main valve plug 7, be turned on and off part or
Throttling through hole on whole guide valve set components, so as to play a part of gently throttling.
As shown in figure 3, give a kind of principle using the slow hydraulic circuit for changing up the flow type balanced valve closed of the present invention
Schematic diagram.In the figure, the slow V hydraulic fluid ports for changing up the flow type balanced valve closed of the A mouths connection present invention of reversal valve, the present invention open slowly
The C hydraulic fluid port connection liquid cylinder pressure rodless cavities of the flow type balanced valve closed soon, the slow X hydraulic fluid ports for changing up the flow type balanced valve closed of the present invention
Oil liquid pressure controlled by operation handle, the present invention is slow, and the Y hydraulic fluid ports for changing up the flow type balanced valve closed are directly connected to fuel tank.The liquid
Push back road at work, including rise, stop and decline these three processes, specific work process is as follows：
(1) uphill process.The pressure oil of reversal valve reaches the V hydraulic fluid ports of flow type balanced valve, and the pressure oil of V hydraulic fluid ports overcomes the
The pretightning forces of two elastic components 13 promotes nonreturn valve core 4 to move right unlatchings, and pressure oil flows into C hydraulic fluid ports arrival hydraulic cylinder through V hydraulic fluid ports
Rodless cavity, promote hydraulic cylinder up.This stage fluid flows into C mouths by V mouths does not have throttling action.
(2) process is declined.The pressure oil of X hydraulic fluid ports is applied on main valve plug 7 into the second control chamber 8, overcomes the first elasticity
The pretightning force of part 2, move to left main valve plug 7.The right-hand member that nonreturn valve core 4 is against the second guide pin bushing 9 has separated V hydraulic fluid ports and C hydraulic fluid ports, C oil
The hydraulic oil of mouth can only flow to V hydraulic fluid ports by the second flow channel hole 14 of the second guide pin bushing 9 with the aperture that communicates on valve pocket 12.When X hydraulic fluid ports
During pressure increase, main valve plug 7 further moves to left, the second guide pin bushing 9 and valve pocket covered in before progressively exposing by the diameter of main valve plug 7
Each throttling through hole communicated on 12 so that area of passage relaxes increase, and load lowering velocity can be with precisely controlled.And because
For many grooves need not be opened on main valve plug 7 as prior art, reducing many processing technologys, processing cost reduces,
And the rigidity of main valve plug 7 will not be had any impact.
(3) stopped process.X hydraulic fluid ports pressure reduces, and the first elastic component 2 promotes main valve plug 7 to move to right, and area of passage gradually contracts
It is small, until the valve port of main valve plug 7 is shut.
Although preferred embodiments of the present invention have been described, but those skilled in the art once know basic creation
Property concept, then can make other change and modification to these embodiments.So appended claims be intended to be construed to include it is excellent
Select embodiment and fall into having altered and changing for the scope of the invention.As long as it will additionally be appreciated that in the absence of in structure
Conflict, the feature in each embodiment can be combined with each other, and the combined type feature formed still falls within the scope of the present invention
It is interior.The invention is not limited in specific embodiment disclosed herein, but all skills including falling within the scope of the appended claims
Art scheme.
Claims (8)
1. a kind of change up the flow type balanced valve closed slowly, it is characterised in that including valve body, main valve plug, nonreturn valve core, guiding valve pocket
Component, one-way damper valve, the first elastic component and the second elastic component, the guide valve set component and valve body are fixedly sleeved in opposite directions, institute
State main valve plug and nonreturn valve core is axially towards one another and is slidably arranged in the guide valve set component, first elastic component is located at valve
Between body and main valve plug, second elastic component is located between guide valve set component and nonreturn valve core；The main valve plug with it is described
Guide valve set component sequentially forms the first control chamber connected with the Y hydraulic fluid ports of valve body and connected with the X hydraulic fluid ports of valve body second
Control chamber；The C hydraulic fluid ports of V hydraulic fluid port and axial direction of the guide valve set component formed with radial direction, the V hydraulic fluid ports are located at main valve plug and list
To the junction of valve element, the C hydraulic fluid ports connect with the fluid course set in the inner chamber of the nonreturn valve core and main valve plug,
The one end of the main valve plug away from C hydraulic fluid ports has been slidably socketed the one-way damper valve；The guide valve covers component close to V hydraulic fluid ports edge
It is axially arranged with multiple throttling through holes；In V hydraulic fluid port oil-feeds, nonreturn valve core is opened, and V hydraulic fluid ports connect with C hydraulic fluid ports；In X hydraulic fluid port oil-feeds
Promote main valve plug vertically to during the movement of the first elastic component direction of compression, the throttling through hole of guide valve set component progressively exposes, institute
Damping hole of the fluid of chamber through the one-way damper valve where stating the first elastic component flows to C hydraulic fluid ports；The main valve plug include according to
Back end cylindrical, first shoulder, the first recess, the second shoulder and the front end of secondary connection, front end is at the second shoulder formed with
Two recesses, second control chamber are that second recess is connected and formed with the first guide pin bushing and the second guide pin bushing；First recess
First shoulder and the second shoulder are connected, and first recess is connected to form the first control chamber with the first guide pin bushing；The main valve plug
The loudspeaker type hole of axial direction is provided with towards one end of the nonreturn valve core, one end is additionally provided with the main valve plug and is connected with loudspeaker type hole
Logical first flow hole and the 3rd oblique hole connected with the other end in first flow hole, the other end of the 3rd oblique hole
First shoulder and back end cylindrical junction positioned at the main valve plug.
2. the flow type balanced valve closed is changed up slowly as claimed in claim 1, it is characterised in that the guide valve set component includes
First guide pin bushing, the second guide pin bushing and valve pocket, the nonreturn valve core are located in one end of the valve pocket, in the middle part of the other end of the valve pocket
Snapped connection with valve body, the other end of the valve pocket is close to end and the second guide pin bushing by positioning pin connection, second guide pin bushing
Formed with recessed position between the valve body, first guide pin bushing be connected to the recessed position and some to the valve
Internal cavity direction extension.
3. the flow type balanced valve closed is changed up slowly as claimed in claim 2, it is characterised in that second guide pin bushing includes shoulder
Portion and insertion section, the front end of the insertion section are provided with multiple first throttle through holes, and the rear end of the insertion section is provided with the first positioning
Pin-and-hole, the valve pocket be provided with corresponded with multiple first throttle through holes of insertion section multiple second connect throttle through holes with
And the second dowel hole corresponding with the first dowel hole.
4. the flow type balanced valve closed is changed up slowly as claimed in claim 3, it is characterised in that the multiple first throttle through hole
It is evenly distributed on the different annular sections of the insertion section front end of second guide pin bushing and along the front end side face arrangement of insertion section, makes
Increasing first throttle through hole and corresponding second throttling are logical when the direction of primary spools to the first elastic component of compression is moved
Hole connects with C hydraulic fluid ports.
5. change up the flow type balanced valve closed slowly as 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 the second oblique hole, the first oblique hole connection Y hydraulic fluid ports and the first control chamber, and described second
Oblique hole connects X hydraulic fluid ports and the second control chamber.
6. the flow type balanced valve closed is changed up slowly as claimed in claim 1, it is characterised in that the nonreturn valve core is towards main valve
The side of core is provided with the internal diameter of conical opening and the conical opening more than the main valve plug end face external diameter towards nonreturn valve core side, in V oil
Mouth does not enter under oil condition, and the main valve plug abuts to the conical opening of the nonreturn valve core and formation in the presence of the first elastic component
Linear sealing and separate V hydraulic fluid ports and C hydraulic fluid ports.
7. the flow type balanced valve closed is changed up slowly as claimed in claim 1, it is characterised in that in the aperture of the loudspeaker type hole
Footpath is equal with the diameter of back end cylindrical, and the external diameter of the front end is equal with the diameter of first shoulder, the diameter of second shoulder
More than the diameter of first shoulder；Spring base and steel ball are provided between the back end cylindrical of first elastic component and main valve plug.
8. the flow type balanced valve closed is changed up slowly as claimed in claim 7, it is characterised in that the one-way damper valve movable sleeve
It is connected on the back end cylindrical, the side face where the one-way damper valve maximum gauge covers the corresponding portion of component with the guide valve
Liquid stream space be present between position, when the main valve plug moves to the nonreturn valve core direction, positioned at the first elastic component institute
Connected in the fluid of chamber through the liquid stream space with C hydraulic fluid ports.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610574689.8A CN106015152B (en) | 2016-07-19 | 2016-07-19 | Slowly the flow type balanced valve closed is changed up |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610574689.8A CN106015152B (en) | 2016-07-19 | 2016-07-19 | Slowly the flow type balanced valve closed is changed up |
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| CN106015152A CN106015152A (en) | 2016-10-12 |
| CN106015152B true CN106015152B (en) | 2017-11-10 |
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Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106438545B (en) * | 2016-10-17 | 2018-01-19 | 浙江华益精密机械股份有限公司 | Load-transducing type balanced valve |
| CN108061070B (en) * | 2017-12-19 | 2019-11-26 | 江苏佳佩环保机械设备有限公司 | A kind of pressure-control valve |
| CN108278240B (en) * | 2018-01-24 | 2020-01-10 | 浙江鸣一阀门科技有限公司 | Automatic adjusting damping valve |
| CN108953266B (en) * | 2018-08-21 | 2020-06-19 | 威海协盈自动化科技有限公司 | Balance valve opened in stages |
| CN108930682B (en) * | 2018-08-22 | 2020-06-26 | 江苏金晟元特种阀门股份有限公司 | Balance valve with improved structure |
| CN108825577B (en) * | 2018-09-21 | 2020-02-11 | 上海辛金路流体技术有限公司 | Balance valve with variable hydraulic control ratio |
| CN109538564B (en) * | 2018-11-23 | 2020-05-19 | 江苏骏森工程机械有限公司 | Proportional balance valve |
| CN110878777B (en) * | 2019-11-28 | 2021-06-01 | 温州英斯蒙特自动化仪表有限公司 | Pressure control valve |
| CN111396389A (en) * | 2020-05-21 | 2020-07-10 | 涌镇液压机械（上海）有限公司 | Cartridge valve for high back pressure circuit |
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| JPS6026871A (en) * | 1983-07-26 | 1985-02-09 | Nippon Denso Co Ltd | Balancing piston type pressure control valve |
| CN101886641A (en) * | 2009-05-12 | 2010-11-17 | 上海立新液压有限公司 | Balanced valve |
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| CN106015152A (en) | 2016-10-12 |
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Effective date of registration: 20171010 Address after: The high-tech economic zone 224000 Jiangsu province Yancheng City Jianhu Road No. 999 Applicant after: Yancheng Haite 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 Wen fan electrical and Mechanical Technology Development Co., Ltd. |
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