CN109751440A - Flow balance valve - Google Patents
Flow balance valve Download PDFInfo
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- CN109751440A CN109751440A CN201711073193.3A CN201711073193A CN109751440A CN 109751440 A CN109751440 A CN 109751440A CN 201711073193 A CN201711073193 A CN 201711073193A CN 109751440 A CN109751440 A CN 109751440A
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- 239000012530 fluid Substances 0.000 claims abstract description 161
- 230000036316 preload Effects 0.000 claims description 24
- 238000013016 damping Methods 0.000 claims description 23
- 230000009471 action Effects 0.000 claims description 4
- 238000009434 installation Methods 0.000 claims description 3
- 238000005516 engineering process Methods 0.000 abstract description 2
- 239000003921 oil Substances 0.000 description 69
- 239000010720 hydraulic oil Substances 0.000 description 14
- 230000000694 effects Effects 0.000 description 9
- 238000010586 diagram Methods 0.000 description 6
- 230000033001 locomotion Effects 0.000 description 6
- 230000007423 decrease Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- 239000007788 liquid Substances 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 239000010426 asphalt Substances 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
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Abstract
The present invention relates to valve technology fields, more particularly to a kind of flow balance valve.Kind flow balance valve includes valve pocket, first valve seat, pressure adjusting structure, first spool, second spool and pilot valve, valve pocket is equipped with the first hydraulic fluid port, second hydraulic fluid port and guide's hydraulic fluid port, first spool one end and pressure adjusting structure against, pressure adjusting structure provides pretightning force, it links and compresses the first spring so that the second spool closes the first oil-through-hole, second spool is equipped with upper second oil-through-hole, the first spool other end is pierced by from the second oil-through-hole and closes the second oil-through-hole, first spool is equipped with third oil-through-hole, third spool is contained in third oil-through-hole, third spool closes third oil-through-hole, the second end of valve pocket is equipped with pilot valve and pilot valve between the second hydraulic fluid port and guide's hydraulic fluid port, pilot valve includes at least first segment, second segment, the first segment of pilot valve partially protrude into third oil-through-hole and with third spool against.
Description
Technical field
The present invention relates to valve technology fields, more particularly to a kind of flow balance valve.
Background technique
In modern project machinery, especially in hoisting machinery.For example, bulk loads equipment, luffing and the machines such as flexible
Structure is in decline, when in direction of motion situation identical with load effect direction, it is necessary to sufficiently large back pressure is set in oil return side,
To balance the load, executive component smooth motion just can guarantee, to improve the stability of hydraulic system.
Balanced valve is the key element in balanced hydraulic circuit.Balanced valve to the stability of hydraulic system overall work, can
There is very big influence by property and system effectiveness.The superiority and inferiority of balance valve performance is directly related to mentioning of loading in balanced valve circuit
It rises, positioning and decline, performance determine the performance of complete machine.
For now, existing balanced valve, dynamic stability performance are poor.When hoisting machinery load it is big when, load pressure
Fluctuation easily causes the fluctuation of flow in balanced valve, and the fluctuation of flow will lead to hydraulic system overall stability variation and can
It is reduced by property.
Summary of the invention
Based on this, it is necessary in view of the above technical problems, provide a kind of flow balance valve that dynamic property is stable.
In order to achieve the above objectives, present invention employs following technical proposals: a kind of flow balance valve includes valve pocket, the first valve
Seat, pressure adjusting structure, the first spool, the second spool and pilot valve, the valve pocket are equipped with the first hydraulic fluid port, the second hydraulic fluid port and guide
Hydraulic fluid port, first hydraulic fluid port are connected to guide's hydraulic fluid port, and the valve pocket has the first end and second end being oppositely arranged, the pressure regulation
The first valve seat is equipped with inside the second end of structure setting valve pocket described in the first end of the valve pocket and first valve seat is located at
Between first hydraulic fluid port and the second hydraulic fluid port, first valve seat is equipped with the first oil-through-hole, and first oil-through-hole is by described first
It is connected between hydraulic fluid port and the second hydraulic fluid port, the first spool and the second spool, described between the pressure adjusting structure and first valve seat
The first spring is equipped between first spool and the second spool, under the action of pressure adjusting structure, the second valve of the first spool direction
Core is mobile and compresses the first spring so that the second spool closes the first oil-through-hole, and second spool is equipped with the upper second logical oil
First hydraulic fluid port is connected to by hole, second oil-through-hole with the first oil-through-hole, and first spool protrudes into second from the second oil-through-hole
It is closed in spool and by second oil-through-hole, first spool is equipped with third oil-through-hole, and the third oil-through-hole is by the
One hydraulic fluid port is connected to the first oil-through-hole, contains third spool in the third oil-through-hole, and the third spool is by the third
Oil-through-hole closing, the second end of the valve pocket is equipped with pilot valve and the pilot valve be located at the second hydraulic fluid port and guide's hydraulic fluid port it
Between, the pilot valve include at least first segment, second segment and, the first segment, second segment, outer diameter are incremented by successively, the elder generation
The first segment of guide valve core partially protrudes into the third oil-through-hole and with third spool against outside the second segment of the pilot valve
Diameter of the diameter less than the second oil-through-hole and the diameter greater than third oil-through-hole.
In this application, by the way that above-mentioned structure is arranged, make to constitute main oil circuit between the second spool and the first valve seat；First
1 grade of oil circuit of auxiliary is constituted between the first segment and third spool of guide valve core；Structure between the second segment of pilot valve and the first spool
At 2 grades of oil circuits of auxiliary.When reversal valve commutation, the oil pressure pressure of the first hydraulic fluid port rises sharply, firstly, the oil pressure pressure of guide's hydraulic fluid port pushes away
Dynamic pilot valve is mobile and pushes third spool open, is connected to third oil-through-hole with the first oil-through-hole, opens 1 grade of oil circuit of auxiliary, from
And be connected to the first hydraulic fluid port with the second hydraulic fluid port by third oil-through-hole, carry out pressure release；Secondly, the oil pressure pressure of guide's hydraulic fluid port pushes
Pilot valve is mobile and pushes the first spool open, so that the second oil-through-hole is connected to the first oil-through-hole, opens 2 grades of oil circuits of auxiliary, from
And the first hydraulic fluid port is connected to the second hydraulic fluid port by the second oil-through-hole, further pressure release；Furthermore when the oil pressure pressure of the second hydraulic fluid port
Power overcomes the pretightning force of the first spring, and the second spool is mobile, opens main oil circuit, to pass through the first oil-through-hole for the first hydraulic fluid port
It is connected to the second hydraulic fluid port.In this process, it is opened due to passing through three steps between the first hydraulic fluid port and the second hydraulic fluid port, it can be to avoid liquid
Phenomena such as pressure impact, so that the dynamic property of flow is stablized, effectively improve hydraulic system overall stability and reliability.
Third spring, preload piece, the third bullet are also contained in the third oil-through-hole in one of the embodiments,
One end of spring and the third spool are against the other end and the preload piece of the third spring are against the preload piece pressure
Contracting third spring simultaneously provides pretightning force, closes the third spool by the third oil-through-hole.
The second end of the valve pocket is equipped with the first chamber of installation pilot valve in one of the embodiments, and described the
Second spring is contained in one chamber, the second spring is set in pilot valve, and the first segment of the pilot valve is from institute
It states and is pierced by first chamber by the second hydraulic fluid port and is protruded into the third oil-through-hole, between the first chamber and guide's hydraulic fluid port
Equipped with throttle orifice a, the throttle orifice b interconnected, the throttle orifice a is connected to guide's hydraulic fluid port, the throttle orifice b with it is described
First chamber connection, the first chamber are connected to second hydraulic fluid port.
By setting throttle orifice a, throttle orifice b and second spring, herein throttle orifice a, throttle orifice b constitute one it is hydraulic
Half-bridge.The pressure for pushing pilot valve mobile is to divide to obtain by this hydraulic half-bridge.According to throttle orifice flow father-in-law's formula:
PPilot pressure=P3×Ra2/(Ra2+Rb2), as Ra=Rb, the steady state pressure that throttle orifice a and throttle orifice b are established, PPilot pressureIt is guide
The half of hydraulic fluid port oil pressure pressure p 3, at this time in the balanced valve opening speed of the first spool by PPilot pressureIt determines.Therefore, pass through this
A hydraulic half-bridge can obtain stable PPilot pressureAnd flow control；So as to opening for stable control the first spool of balanced valve
Speed (aperture) is opened, the flow of balanced valve is accurately controlled.Meanwhile the setting of throttle orifice b, it can control the reset of pilot valve
Speed, it can be achieved that soft closing effect.
It is equipped between the first chamber and the second hydraulic fluid port by first chamber and the second hydraulic fluid port in one of the embodiments,
Between the throttle orifice c that is connected to, be axially arranged with blind hole of the pilot valve far from first segment, the blind hole and guide's hydraulic fluid port
Connection contains throttling plug in blind hole, and on throttling plug, the inner wall of the blind hole is equipped with section for the throttle orifice b setting
Discharge orifice d, the throttle orifice d will be interconnected between the blind hole and first chamber.
It is slidably connected between first spool and the second spool in one of the embodiments, first spool leans on
Successively at least provided with first axis of cone and second axis of cone, the maximum outside diameter of first axis of cone is less than institute for one end of nearly second spool
The minimum outer diameter of second axis of cone is stated, first axis of cone is pierced by from second oil-through-hole, and second axis of cone is by described second
Oil-through-hole closing.
By setting first axis of cone and second axis of cone, and due to first axis of cone, second axis of cone outer diameter from far from the
Successively decrease one end of two spools to one end close to the second spool.Therefore the stroke control for extending the unlatching of the first spool, so that control
Flow resolution ratio with higher processed, so that it is good to open low noise, flow accuracy height, stability when the first spool is opened.
Second spool is axially arranged with second oil-through-hole in one of the embodiments, in the second spool
Inside be equipped with the second chamber that be connected to second oil-through-hole, the side wall of second spool is equipped with throttle orifice e, the section
Discharge orifice e will be connected between first hydraulic fluid port and the second chamber, and first spool is equipped with throttle orifice g, the throttling
The second chamber is connected to by hole g with third oil-through-hole
The area of section S1 of second oil-through-hole in one of the embodiments, the area of section of guide's hydraulic fluid port
The range of S2, S1: S2 are as follows: 1: 90≤S1: S2≤1: 10.
It is equipped at least first conical surface and second conical surface in the inner wall of the first oil-through-hole in one of the embodiments, it is described
The cone angle of first conical surface is greater than the cone angle of second conical surface.
Third spring, preload piece, the preload piece are also contained in the third oil-through-hole in one of the embodiments,
It is equipped with dynamic antivibration structure.
When first hydraulic fluid port is connected to the second hydraulic fluid port and is in steady state in flow；That is, choke area reaches maximum
When position, when the first hydraulic fluid port oil pressure pressure continues to increase, it will lead to corresponding flow and increase.At this point, pilot valve is in the oil pressure
Under the action of pressure, there can be the trend for pushing the second spool to open the first oil-through-hole, cause the fluctuation of flow；And dynamic is set
Damping structure, when the first hydraulic fluid port oil pressure pressure continues to increase, dynamic antivibration structure is by pushing third spool, the logical oil of limitation third
The flow of oil liquid in hole under oil pressure pressure effect, can have to increase the oil pressure pressure of third oil-through-hole and push the first valve
Core, and the second spool is driven, so that the second spool closes the trend of the first oil-through-hole.In this way, being increased with offsetting the first hydraulic fluid port
Oil pressure pressure guarantee the stability of hydraulic system to make the output of flow constant.
The dynamic antivibration structure includes the first damping being arranged on the preload piece in one of the embodiments,
Hole and the second damping hole are connected between first damping hole and the second damping hole, and first damping hole and the third are logical
Oilhole connection.
Compared with the prior art, the advantages of the present invention are as follows:
By the way that above-mentioned structure is arranged, make to constitute main oil circuit between the second spool and the first valve seat；The of pilot valve
1 grade of oil circuit of auxiliary is constituted between one section and third spool；2 grades of oil of auxiliary are constituted between the second segment of pilot valve and the first spool
Road.When reversal valve commutation, the oil pressure pressure of the first hydraulic fluid port rises sharply, firstly, the oil pressure pressure of guide's hydraulic fluid port pushes pilot valve
Third spool is moved and pushed open, is connected to third oil-through-hole with the first oil-through-hole, 1 grade of oil circuit of auxiliary is opened, to pass through third
First hydraulic fluid port is connected to by oil-through-hole with the second hydraulic fluid port, carries out pressure release；Secondly, the oil pressure pressure of guide's hydraulic fluid port pushes pilot valve to move
The first spool is moved and pushed open, so that the second oil-through-hole is connected to the first oil-through-hole, 2 grades of oil circuits of auxiliary are opened, to pass through second
First hydraulic fluid port is connected to by oil-through-hole with the second hydraulic fluid port, further pressure release；Furthermore when the oil pressure pressure of the first hydraulic fluid port and the second hydraulic fluid port
It when power difference can overcome the pretightning force of the first spring, pushes the second spool mobile, opens main oil circuit, to pass through the first logical oil
First hydraulic fluid port is connected to by hole with the second hydraulic fluid port.In this process, due to being opened between the first hydraulic fluid port and the second hydraulic fluid port by three steps
It opens, can be to avoid hydraulic shock phenomena such as, so that the dynamic property of flow is stablized, effectively improves hydraulic system monolithic stability
Property and reliability.
Detailed description of the invention
Fig. 1 is structural schematic diagram provided by the invention.
Fig. 2 is enlarged drawing at A in Fig. 1 provided by the invention.
Fig. 3 is pilot valve structural schematic diagram provided by the invention.
Fig. 4 is enlarged drawing at B in Fig. 1 provided by the invention.
Fig. 5 is the first valve seat construction schematic diagram provided by the invention.
Fig. 6 is the second valve core structure schematic diagram provided by the invention.
Fig. 7 is the first valve core structure schematic diagram provided by the invention.
Fig. 8 is the first spool provided by the invention, the second spool, pilot valve assembly structure diagram.
In figure, valve pocket 10, first end 10a, first end 10b, the first hydraulic fluid port 101, the second hydraulic fluid port 102, guide's hydraulic fluid port 103,
First chamber 110, second spring 111, ring baffle 120, throttling gasket 130, the second valve seat 140, the first valve seat 20, first are logical
Oilhole 210, the first conical surface 210a, the second conical surface 210b, pressure adjusting structure 30, screw rod 310, locking nut 320, preloading spring 330,
Locking head 340, adjusting rod 350, the first spool 40, the first spring 401, mounting hole 402, third oil-through-hole 410, third spool
411, third spring 412, preload piece 413, first axis of cone 420, second axis of cone 430, the second spool 50, the second oil-through-hole 510,
Two chambers 520, pilot valve 60, blind hole 601, throttling plug 602, valve ball 603, first segment 610, second segment 620, third section
630, the 4th section 640, dynamic antivibration structure 70, the first damping hole 701, the second damping hole 702, throttle orifice a, throttle orifice b, throttling
Hole c, throttle orifice d, throttle orifice f, throttle orifice g.
Specific embodiment
The present invention will be further described in detail with reference to the accompanying drawings and detailed description.
As shown in Figure 1, the present embodiment provides a kind of flow balance valve, which are mainly applied in modern project machinery, especially
It is and stable flow to be provided for hoisting machinery in hoisting machinery.
The flow balance valve include valve pocket 10, the first valve seat 20, pressure adjusting structure 30, the first spool 40, the second spool 50 and
Pilot valve 60.The first hydraulic fluid port 101, the second hydraulic fluid port 102 and guide's hydraulic fluid port 103 are equipped on valve pocket 10.First hydraulic fluid port 101 and elder generation
Oil diverting port 103 is connected to.Second hydraulic fluid port 102 is between the first hydraulic fluid port 101 and guide's hydraulic fluid port 103.It should be noted that of the invention
When in use, when hoisting machinery zero load, hydraulic oil is from 102 oil inlet of the second hydraulic fluid port, and from 102 oil return of the second hydraulic fluid port；Work as lifting
When mechanical load, and in the direction of motion of hoisting machinery situation identical with load effect direction, commutate through reversal valve, hydraulic oil
From 101 oil inlet of the first hydraulic fluid port, and from 102 oil return of the second hydraulic fluid port.
Preferably, the first hydraulic fluid port 101 and the second hydraulic fluid port 102 are arranged on the periphery of valve pocket 10 and along the diameter of valve pocket 10
It is arranged to interval, the axial direction of valve pocket 10 is arranged in guide's hydraulic fluid port 103.Referring specifically to Fig. 1, in the present embodiment, valve pocket 10 has
There are the first end 10a and second end 10b being oppositely arranged, the second end 10b of valve pocket 10 is arranged in guide's hydraulic fluid port 103.
The first end 10a of valve pocket 10 is arranged in pressure adjusting structure 30, and 30 partial receipt of pressure adjusting structure is in the valve pocket 10.
The second end 10b of the valve pocket 10 is equipped with the first valve seat 40, and the first valve seat 20 is located at the first hydraulic fluid port 101 and the second hydraulic fluid port 102
Between.First valve seat 20 is embedded in valve pocket 10 preferably in a manner of interference.First valve seat 20 is equipped with the first oil-through-hole 210.First is logical
Oilhole 210 will be connected between first hydraulic fluid port 101 and the second hydraulic fluid port 102.The first spool 40 and the second spool are additionally provided in valve pocket 10
50, the second spool 50 is between the first valve seat 20 and the first spool 40, and the first spool 40 and the second spool 50 being capable of edges
The axially opposing sliding of valve pocket 10.First spool 40 has opposite both ends, and wherein one end of the first spool 40 protrudes into second
It is slidably connected in spool 50 and with the second spool 50.The wherein other end of first spool 40 is abutted with pressure adjusting structure 30, the second valve
One end of core 50 towards the first valve seat 20 is abutted with the first valve seat 20, and the second spool 50 is for closing the first oil-through-hole 210.
First oil-through-hole 210 is closed in order to ensure the second spool 50 is abutted with the second valve seat 20, the first spool 40 and
The first spring 401 is equipped between two spools 50.By adjusting pressure adjusting structure 30, provide pressure adjusting structure 30 to the first spool 40 pre-
Clamp force keeps the first spool 40 mobile towards the second spool 50 and compresses the first spring 401, and the first spring 401 oppresses the second spool
50 fit closely the end face of the second spool 50 with the second valve seat 20, and the first oil-through-hole 210 is closed.I.e., it is possible to understand, first
Hydraulic oil is not turned between hydraulic fluid port 101 and the second hydraulic fluid port 102.Second spool 50 is equipped with upper second oil-through-hole 510.Second oil-through-hole
510 will be connected between first hydraulic fluid port 101 and the first oil-through-hole 210.One end for protruding into the second spool 50 of first spool 40 is from
Two oil-through-holes 510 are pierced by and close the second oil-through-hole 510.I.e., it is possible to understand, 210 envelope of the first hydraulic fluid port 101 and the first oil-through-hole
It closes, that is, not in conducting hydraulic oil between the first hydraulic fluid port 101 and the first oil-through-hole 210.First spool 40 is logical equipped with third
Oilhole 410.First hydraulic fluid port 101 is connected to by third oil-through-hole 410 with the first oil-through-hole 210.Is contained in third oil-through-hole 410
Three spools 411.Third spool 411 closes third oil-through-hole 410.I.e., it is possible to understand, the first hydraulic fluid port 101 and the first oil-through-hole
210 partitions, that is, the first hydraulic fluid port 101 and the first oil-through-hole 210 be not in conducting hydraulic oil.
Secondly, the second end 10b of valve pocket 10 is equipped with pilot valve 60 in conjunction with Fig. 1, Fig. 3 and Fig. 6.Pilot valve 60
Between the second hydraulic fluid port 102 and guide's hydraulic fluid port 103.Pilot valve 60 includes at least first segment 610, second segment 620 and third section
630.The first segment 610, second segment 620,630 outer diameter of third section are incremented by successively.Preferably, pilot valve 60 is ladder circle
Axis forms first shaft shoulder, forms second shaft shoulder between second segment 620 and third section 630 between first segment 610 and second segment 620.
In the present embodiment, the first segment 610 of pilot valve 60 partially protrude into third oil-through-hole 410 and with third spool 411 against；
Diameter of 620 outer diameter of second segment of pilot valve 60 less than the second oil-through-hole 510 and the diameter greater than third oil-through-hole 410.First
630 outer diameter of third section of guide valve core 60 is greater than the diameter of the second oil-through-hole 510.
In the present embodiment, when hoisting machinery loads, the first hydraulic fluid port 101 is load port, and the second hydraulic fluid port 102 is oil return
Mouthful, guide's hydraulic fluid port 103 is vertically arranged with the first hydraulic fluid port 101 and the second hydraulic fluid port 102.And the pressure of load port acts on always and oil circuit
The direction that channel is closed.Even if the first spring 401 is pressed down, asphalt channel still can be with normal switching-off.In this way, not only increasing
The safety of system, and advantageously reduce load port pressure oscillation and cause flowed fluctuation.
In the present embodiment, main oil circuit is constituted between the second spool 50 and the first valve seat 20；The first of pilot valve 60
1 grade of oil circuit of auxiliary is constituted between section 610 and third spool 411；Structure between the second segment 620 of pilot valve 60 and the first spool 40
At 2 grades of oil circuits of auxiliary.When hoisting machinery load, and the situation that the direction of motion of hoisting machinery is identical as load effect direction
Under, it commutates through reversal valve, hydraulic oil is from 101 oil inlet of the first hydraulic fluid port.When the oil pressure pressure of the first hydraulic fluid port 101 rises sharply, the first hydraulic fluid port
101 middle part liquid separation pressure oils push pilot valve 60 mobile, at this time by guide's hydraulic fluid port, and under the effect of the oil pressure of the hydraulic oil
The first segment 610 of pilot valve opens third spool 411, so that it is connected to third oil-through-hole 410 with the first oil-through-hole 210,
Open 1 grade of oil circuit of auxiliary, the hydraulic oil of the first hydraulic fluid port 101 by third oil-through-hole 410 flows through the first oil-through-hole 210 and from second
102 oil return box of hydraulic fluid port carries out pressure release.Secondly, the oil pressure pressure of guide's hydraulic fluid port 103 pushes pilot valve 60 further to move,
First shaft shoulder is resisted against 410 outer wall of third oil-through-hole at this time.The oil pressure pressure of guide's hydraulic fluid port 103 overcomes the preload of pressure adjusting structure
Power pushes the first spool 40 open, so that the second oil-through-hole 510 is connected to the first oil-through-hole 210, opens and assists 2 grades of oil circuits, and first
The hydraulic oil of hydraulic fluid port by the second oil-through-hole 510 flows through the first oil-through-hole 210 and from 102 oil return box of the second hydraulic fluid port, carries out pressure release.
Furthermore when the pressure difference between the first hydraulic fluid port 101 and the second hydraulic fluid port 102 can overcome the pretightning force of the first spring, second is pushed
Spool 50 is mobile, opens main oil circuit, makes to be connected to the first hydraulic fluid port 101 with the second hydraulic fluid port 102 by the first oil-through-hole 210, the
The hydraulic oil of one hydraulic fluid port, from 102 oil return box of the second hydraulic fluid port, carries out pressure release by the first oil-through-hole 210.In this process, due to
It is opened between first hydraulic fluid port 101 and the second hydraulic fluid port 102 by three steps, can be to avoid hydraulic shock phenomena such as, so that flow is dynamic
State property can be stablized, and hydraulic system overall stability and reliability are effectively improved.
Specifically, open auxiliary 1 grade of oil circuit when, hydraulic oil from the first hydraulic fluid port 101 into, through throttle orifice e, second chamber 412,
And it throttle orifice g, is connected to the first oil-through-hole 210 by third oil-through-hole 410.When starting to assist 2 grades of oil circuits, hydraulic oil is from the
One hydraulic fluid port 101 through throttle orifice e, second chamber 412, with the first oil-through-hole 210 into being connected to.
Preferably, in the present embodiment, Fig. 4 is referred to, third spring 412, pre- is also contained in third oil-through-hole 410
Tight part 413.One end of third spring 412 and third spool 411 are against the other end of third spring 412 and the preload piece 413
Against；Preload piece 413 compresses third spring 412 and provides pretightning force to third spool 411, makes third spool 411 by the third
Oil-through-hole 410 is closed.
In the present embodiment, Fig. 2 and Fig. 3 are referred to, the second end 10b of valve pocket 10 is equipped with the first of installation pilot valve 60
Chamber 110.Pilot valve 60 is equipped with the 4th section 640 far from first segment 610, and described 4th section sliding between 640 and first chamber 110
Dynamic connection.Second spring 111 is contained in first chamber 110, second spring 111 is set in pilot valve 60.Pilot valve
The first segment 610 of core 60 in first chamber 110 from being pierced by by the second hydraulic fluid port 102 and protrude into the third oil-through-hole 410.The
Throttle orifice a, the throttle orifice b interconnected is equipped between one chamber 110 and guide's hydraulic fluid port 103.Further, throttle orifice a and elder generation
Oil diverting port 103 is connected to, and throttle orifice b is connected to first chamber 110, and first chamber 110 is connected to the second hydraulic fluid port 102.
Further, throttle orifice c is equipped between first chamber 110 and the second hydraulic fluid port 102.Throttle orifice c is by first chamber
It is connected between 110 and the second hydraulic fluid port 102.Blind hole 601 is axially arranged with far from first segment 610 in pilot valve 60.Blind hole 601 with
Guide's hydraulic fluid port 103 is connected to, and throttling plug 602 is contained in blind hole 601.Throttle orifice b setting is on throttling plug 602.Blind
The inner wall in hole 601 is equipped with throttle orifice d, and the throttle orifice d will be interconnected between the blind hole 601 and first chamber 110.
Preferably, the third shaft shoulder is formed between 640 and third section 630 at the 4th section.Second spring 111 is set in third section
On 630.The ring baffle 120 between first chamber 110 and the second hydraulic fluid port 102, above-mentioned ring baffle 120 are equipped with throttle orifice
c.One end of second spring 111 is resisted against on ring baffle 120, and the other end of second spring 111 is resisted against on the third shaft shoulder.?
The second end 10b of valve pocket 10 is equipped with throttling gasket 130, throttles and surrounds above-mentioned first between gasket 130 and ring baffle 120
Chamber 110.Throttle orifice a setting is on throttling gasket 130.
Valve ball 603 is equipped in blind hole 601.Bypass check valve is constituted between blind hole 601, valve ball 603.Bypass check valve
Effect is when preventing pilot valve 50 from closing, the hydraulic oil of the second hydraulic fluid port 102 to be prevented to be back to the second chamber from throttle orifice c
Room, oil circuit string oil cause to malfunction.
In the present embodiment, throttle orifice a, throttle orifice b, second spring 111 constitute a hydraulic half-bridge.And push guide
The mobile P of spool 60Pilot pressureIt is to divide to obtain by this hydraulic half-bridge.According to throttle orifice flow father-in-law's formula: PPilot pressure=P3×
Ra2/(Ra2+Rb2), as Ra=Rb, the steady state pressure that throttle orifice a and throttle orifice b are established, PPilot pressureIt is 103 oil pressure of guide's hydraulic fluid port
The half of pressure p 3, at this time in the balanced valve opening speed of the first spool 40 by PPilot pressureIt determines.Therefore, hydraulic by this
Half-bridge can obtain stable PPilot pressureAnd flow control；So as to the unlatching speed of stable control the first spool of balanced valve 40
Degree, accurately controls the flow of balanced valve.Meanwhile the setting of throttle orifice b, it can control the reset speed of pilot valve 60, it can
Realize the effect of soft closing.
Herein, it should be explained that: P3It indicates: guide's hydraulic fluid port oil pressure pressure.The diameter of Ra expression throttle orifice a.
The diameter of Rb expression throttle orifice b.The area of section S1 of second oil-through-hole, the area of section S2 of guide's hydraulic fluid port, it is described
S1: S2 range are as follows: 1: 90≤S1: S2≤1: 10
In the present embodiment, referring to Fig. 3 and Fig. 6, the area of section S1 of second oil-through-hole, section of guide's hydraulic fluid port
Face area S2, described S1: S2 range are as follows: 1: 90≤S1: S2≤1: 10.The diameter of second oil-through-hole is R1, guide's hydraulic fluid port
Diameter is R2.Due to S1=2 π R2.Therefore, R1: R2 is directly proportional to S1: S2.Due to, F=PS, 1: 90≤S1: S2≤1: 10.It can
To understand, the oil pressure pressure of guide's hydraulic fluid port is much larger than effect of first hydraulic fluid port to the second oil-through-hole to the active area of pilot valve
Area.So the first hydraulic fluid port almost can be ignored the active force of pilot valve.So the oil pressure pressure of guide's hydraulic fluid port
The position of the first spool 40 is determined with pilot valve, and determines the opening degree between the first hydraulic fluid port 101 and the second hydraulic fluid port 102.
In the present embodiment, Fig. 7 is referred to, in the first spool 40 close to one end of the second spool 50 at least provided with the first cone
Axis 420 and second axis of cone 430.First axis of cone 420 is located at second axis of cone, 430 outside.First axis of cone 420, second axis of cone
430 outer diameter successively successively decreases from one end far from the second spool 50 to one end close to the second spool 50, and first axis of cone 420
Maximum outside diameter less than second axis of cone 430 minimum outer diameter.Further, first axis of cone 420 is pierced by from the second oil-through-hole 510,
The periphery of second axis of cone 430 closes the second oil-through-hole 510.
Specifically, the first spool 40 is distributed in three-stage multi-diameter shaft.Including the first multi-diameter shaft, the second multi-diameter shaft, third rank
The end face of terraced axis, maximum simultaneously the first multi-diameter shaft of the diameter of axle of the first multi-diameter shaft leans with pressure adjusting structure, the diameter of axle of third multi-diameter shaft
It is minimum.First multi-diameter shaft forms the first ladder shaft shoulder between the second multi-diameter shaft.One end of first spring 401 is resisted against the first rank
On the terraced shaft shoulder, the other end of the first spring 401 is resisted against on the second spool 50.
More specifically, being equipped with first axis of cone 420 and second axis of cone far from one end of the first multi-diameter shaft in third multi-diameter shaft
430.The cone-apex angle of first axis of cone 420 is between 80-100 degree；The cone-apex angle of second axis of cone 430 be 10-20 degree it
Between.And by two sections of different cone angles of setting, to keep the area change of gradient of the second oil-through-hole small, to reach fine control
Flow, so that noise is lower when 2 grades of oil circuits of auxiliary are opened, flow control is finer and flow control is more stable.Secondly, the
The length of one axis of cone 420 is set as between 2-4mm, so that the stroke control of the first spool 40 is longer, to make to control flow tool
There is higher resolution ratio.
In the present embodiment, figure Fig. 5 is referred to, is axially arranged with the second oil-through-hole 510 in the second spool 50.Second logical oil
Hole 510 axially penetrates through the setting of the second spool 50.Third multi-diameter shaft is pierced by from the second oil-through-hole 510, and the second multi-diameter shaft and
While being slidably connected between two oil-through-holes 510 and it is tightly connected.It is equipped with and the second oil-through-hole 510 in the inside of the second spool 50
The second chamber 520 of connection.Throttle orifice e is equipped in the side wall of the second spool 50.By throttle orifice e by the first hydraulic fluid port 101 and
It is connected between two chambers 520.
Preferably, throttle orifice e has 4, and 4 throttle orifice e are evenly distributed on the side wall of the second spool 50.Each
Angle between the axis of throttle orifice e and the axis of the second spool 50 is 45 degree.
In the present embodiment, it is equipped at least the first conical surface 210a and the second conical surface 210b in the inner wall of the first oil-through-hole 210,
The cone-apex angle of first conical surface 210a is between 90-110 degree, and the cone-apex angle of second conical surface 210b is between 20-40 degree.
Second slide valve 50 is resisted against on the first conical surface 210a.Herein, by the inner wall in the first oil-through-hole 210 equipped at least first cone
Face 210a and the second conical surface 210b improves flow gain in the first oil-through-hole 210 so as to imitate, and improves the first oil-through-hole
210 area change gradient makes the amount of opening of the first oil-through-hole 210 have certain buffering, so that flow gradients be made to reduce, improves
Throttle feature, enhances the stability of hydraulic system, to keep balanced valve decline control speed controllable.
In the present embodiment, referring again to Fig. 1, the pressure adjusting structure 30 includes screw rod 310, locking nut 320, pre-tightens bullet
Spring 330, locking head 340, adjusting rod 350.The first end 10a of the valve pocket 10 is equipped with the second valve seat 140, second valve seat
It is interference fitted between 140 and the first end 10a of valve pocket 10.Adjusting rod is successively arranged between the valve pocket 10 and the second valve seat 140
350, locking head 340, the preloading spring 330 is set on adjusting rod 350, and one end of the preloading spring 330 is resisted against
First spool 40, the other end of preloading spring 330 are resisted against on locking head 340.Described 310 one end of screw rod is resisted against locking head
340, the other end of screw rod 310 is located at the outside of the second valve seat 140.The screw rod 310 is adjusted, screw rod 310 pushes locking head 340
Preloading spring is compressed, to provide pretightning force to the first spool.
Preferably, mounting hole 402 is axially arranged in the first spool 40, one end of adjusting rod 350 is loaded on mounting hole 402
In.The mounting hole 402 is connected to third oil-through-hole 410.It is interference fitted between 413 one end of preload piece and third oil-through-hole 410.
One end of adjusting rod 350 is loaded in mounting hole 402 and has gap 703 between preload piece 413.
In the present embodiment, referring to Figure 1, Fig. 3 and Fig. 7, third spring is also contained in third oil-through-hole 410
412, preload piece 413 are equipped with dynamic antivibration structure 70 on preload piece 413.
Specifically, dynamic antivibration structure 70 includes the first damping hole 701 and second being arranged on the preload piece 413
Damping hole 702 is connected between first damping hole 701 and the second damping hole 702.First damping hole 701 and described the
The connection of three oil-through-holes 410.Throttle orifice f is equipped in the inner wall of third spring 412, and the throttle orifice f is by third oil-through-hole 410 and the
The connection of one hydraulic fluid port 101.
Further, preload piece 413 is axially arranged with the first damping hole 701, and preload piece 413 is radially provided with the second damping
Hole 702.It is connected between second damping hole 702 and gap.
When the first hydraulic fluid port 101 is connected to the second hydraulic fluid port 102 and flow is at steady state, that is, choke area
When reaching maximum position.When 101 oil pressure pressure of the first hydraulic fluid port continues to increase, it will lead to corresponding flow and increase.Pilot valve 60
Under the action of the oil pressure pressure, there can be the movement tendency for pushing the second spool 50 to open the first oil-through-hole 210, cause flow
Fluctuation；And at this point, the hydraulic oil of the first hydraulic fluid port 101 after throttle orifice f enters third oil-through-hole 410, is successively hindered from first
Buddhist nun hole 701 enters in the second damping hole 702.Oil pressure pressure in second damping hole 702 acts on preload piece 413, to make
First spool 40 is whole to be had to the closed movement tendency of the first oil-through-hole 210.In this way, the first hydraulic fluid port is offset
The 101 oil pressure pressure increased, so that the output of flow constant, guarantees the stability of hydraulic system.
Each technical characteristic of embodiment described above can be combined arbitrarily, for simplicity of description, not to above-mentioned reality
It applies all possible combination of each technical characteristic in example to be all described, as long as however, the combination of these technical characteristics is not deposited
In contradiction, all should be considered as described in this specification.
The embodiments described above only express several embodiments of the present invention, and the description thereof is more specific and detailed, but simultaneously
It cannot therefore be construed as limiting the scope of the patent.It should be pointed out that coming for those of ordinary skill in the art
It says, without departing from the inventive concept of the premise, various modifications and improvements can be made, these belong to protection of the invention
Range.Therefore, the scope of protection of the patent of the invention shall be subject to the appended claims.
Claims (10)
1. a kind of flow balance valve, including valve pocket, the first valve seat, pressure adjusting structure, the first spool, the second spool and pilot valve,
The valve pocket is equipped with the first hydraulic fluid port, the second hydraulic fluid port and guide's hydraulic fluid port, and the valve pocket has the first end and second being oppositely arranged
End, the pressure adjusting structure, which is arranged in inside the second end of valve pocket described in the first end of the valve pocket, is equipped with the first valve seat and described the
For one valve seat between the first hydraulic fluid port and the second hydraulic fluid port, first valve seat is equipped with the first oil-through-hole, first oil-through-hole
It will be connected between first hydraulic fluid port and the second hydraulic fluid port, it is characterised in that: between the pressure adjusting structure and first valve seat
One spool and the second spool are equipped with the first spring, under the action of pressure adjusting structure, institute between first spool and the second spool
It is mobile towards the second spool and compress the first spring so that the second spool closes the first oil-through-hole to state the first spool, described second
Spool is equipped with upper second oil-through-hole, and the first hydraulic fluid port is connected to by second oil-through-hole with the first oil-through-hole, first spool from
Second oil-through-hole protrudes into the second spool and closes second oil-through-hole, and first spool is equipped with third oil-through-hole,
First hydraulic fluid port is connected to by the third oil-through-hole with the first oil-through-hole, and third spool is contained in the third oil-through-hole, described
Third spool closes the third oil-through-hole, and the second end of the valve pocket is equipped with pilot valve and the pilot valve is located at the
Between two hydraulic fluid ports and guide's hydraulic fluid port, the pilot valve include at least first segment, second segment and, it is the first segment, second segment, outer
Diameter is incremented by successively, and the first segment of the pilot valve partially protrudes into the third oil-through-hole and with third spool against described
Diameter of the second segment outer diameter of pilot valve less than the second oil-through-hole and the diameter greater than third oil-through-hole.
2. flow balance valve according to claim 1, which is characterized in that also contain third bullet in the third oil-through-hole
Spring, preload piece, one end of the third spring and the third spool are against the other end of the third spring and the preload
Part is against the preload piece compresses third spring and provides pretightning force, closes the third spool by the third oil-through-hole.
3. flow balance valve according to claim 1, which is characterized in that the second end of the valve pocket is equipped with installation pilot valve
The first chamber of core contains second spring in the first chamber, and the second spring is set in pilot valve, the elder generation
The first segment of guide valve core in the first chamber from being pierced by by the second hydraulic fluid port and protrude into the third oil-through-hole, described first
The throttle orifice a, throttle orifice b, the throttle orifice a and guide's hydraulic fluid port interconnected is equipped between chamber and guide's hydraulic fluid port to connect
Logical, the throttle orifice b is connected to the first chamber, and the first chamber is connected to second hydraulic fluid port.
4. flow balance valve according to claim 3, which is characterized in that be equipped between the first chamber and the second hydraulic fluid port
The throttle orifice c that will be connected between first chamber and the second hydraulic fluid port, be axially arranged with blind hole of the pilot valve far from first segment, institute
It states blind hole to be connected to guide's hydraulic fluid port, throttling plug is contained in blind hole, the throttle orifice b setting is throttling on plug,
The inner wall of the blind hole is equipped with throttle orifice d, and the throttle orifice d will be interconnected between the blind hole and first chamber.
5. flow balance valve according to claim 1, which is characterized in that slided between first spool and the second spool
Connection, first spool is close to one end of the second spool successively at least provided with first axis of cone and second axis of cone, first cone
The maximum outside diameter of axis is less than the minimum outer diameter of second axis of cone, and first axis of cone is pierced by from second oil-through-hole, described
Second axis of cone closes second oil-through-hole.
6. flow balance valve according to claim 1, which is characterized in that second spool is axially arranged with described the
Two oil-through-holes are equipped with the second chamber being connected to second oil-through-hole, the side of second spool in the inside of the second spool
Wall is equipped with throttle orifice e, and the throttle orifice e will be connected between first hydraulic fluid port and the second chamber, on first spool
Equipped with throttle orifice g, the second chamber is connected to by the throttle orifice g with third oil-through-hole.
7. flow balance valve according to claim 1, which is characterized in that the area of section S1 of second oil-through-hole, institute
State the range of the area of section S2, S1:S2 of guide's hydraulic fluid port are as follows: 1:90≤S1:S2≤1:10.
8. flow balance valve according to claim 1, which is characterized in that be equipped at least first in the inner wall of the first oil-through-hole
The conical surface and second conical surface, the cone angle of first conical surface are greater than the cone angle of second conical surface.
9. flow balance valve according to claim 1-8, which is characterized in that also accommodated in the third oil-through-hole
There are third spring, preload piece, the preload piece is equipped with dynamic antivibration structure.
10. flow balance valve according to claim 9, which is characterized in that the dynamic antivibration structure includes being arranged in institute
The first damping hole and the second damping hole on preload piece are stated, is connected between first damping hole and the second damping hole, described
One damping hole is connected to the third oil-through-hole.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711073193.3A CN109751440B (en) | 2017-11-04 | 2017-11-04 | Flow balance valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711073193.3A CN109751440B (en) | 2017-11-04 | 2017-11-04 | Flow balance valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109751440A true CN109751440A (en) | 2019-05-14 |
| CN109751440B CN109751440B (en) | 2023-11-07 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711073193.3A Active CN109751440B (en) | 2017-11-04 | 2017-11-04 | Flow balance valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109751440B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112253819A (en) * | 2020-09-07 | 2021-01-22 | 北京航天石化技术装备工程有限公司 | Double-conical-surface sealing structure for safety valve and application thereof |
| CN113074029A (en) * | 2021-04-14 | 2021-07-06 | 浙江尔格科技股份有限公司 | Oil pump pressure reducing valve and oil pump for internal combustion engine using same |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0710509U (en) * | 1993-07-30 | 1995-02-14 | 古河機械金属株式会社 | Counter balance valve |
| CN106195370A (en) * | 2016-08-13 | 2016-12-07 | 李军 | Cartridge balanced valve |
| CN205841934U (en) * | 2016-07-22 | 2016-12-28 | 大唐南京发电厂 | A kind of multiple anti-internal hemorrhage due to trauma air relief valve of hp and lp bypass |
| CN206234447U (en) * | 2016-09-29 | 2017-06-09 | 浙江华益精密机械股份有限公司 | Pilot-operated type balanced valve |
-
2017
- 2017-11-04 CN CN201711073193.3A patent/CN109751440B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0710509U (en) * | 1993-07-30 | 1995-02-14 | 古河機械金属株式会社 | Counter balance valve |
| CN205841934U (en) * | 2016-07-22 | 2016-12-28 | 大唐南京发电厂 | A kind of multiple anti-internal hemorrhage due to trauma air relief valve of hp and lp bypass |
| CN106195370A (en) * | 2016-08-13 | 2016-12-07 | 李军 | Cartridge balanced valve |
| CN206234447U (en) * | 2016-09-29 | 2017-06-09 | 浙江华益精密机械股份有限公司 | Pilot-operated type balanced valve |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112253819A (en) * | 2020-09-07 | 2021-01-22 | 北京航天石化技术装备工程有限公司 | Double-conical-surface sealing structure for safety valve and application thereof |
| CN112253819B (en) * | 2020-09-07 | 2022-07-05 | 北京航天石化技术装备工程有限公司 | Double-conical-surface sealing structure for safety valve and application thereof |
| CN113074029A (en) * | 2021-04-14 | 2021-07-06 | 浙江尔格科技股份有限公司 | Oil pump pressure reducing valve and oil pump for internal combustion engine using same |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109751440B (en) | 2023-11-07 |
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Address after: 689 Jiefang Road, Diankou Industrial Zone, Zhuji County, Shaoxing City, Zhejiang Province Applicant after: Zhejiang Huayi Precision Machinery Co.,Ltd. Address before: 689 Jiefang Road, Diankou Industrial Zone, Zhuji County, Shaoxing City, Zhejiang Province Applicant before: ZHEJIANG HUAYI PRECISION MACHINERY Co.,Ltd. |
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Effective date of registration: 20231025 Address after: 311800 Diankou Town Industrial Zone, Zhuji City, Shaoxing City, Zhejiang Province Patentee after: Zhejiang Sanshang Zhidi Technology Co.,Ltd. Address before: No. 689 Jiefang Road, Zhuji County, Shaoxing, Zhejiang Patentee before: Zhejiang Huayi Precision Machinery Co.,Ltd. |