CN1300499C - Ratio pressure difference control valve - Google Patents
Ratio pressure difference control valve Download PDFInfo
- Publication number
- CN1300499C CN1300499C CNB2003101227851A CN200310122785A CN1300499C CN 1300499 C CN1300499 C CN 1300499C CN B2003101227851 A CNB2003101227851 A CN B2003101227851A CN 200310122785 A CN200310122785 A CN 200310122785A CN 1300499 C CN1300499 C CN 1300499C
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- valve body
- crosspassage
- spool
- valve
- passage
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Abstract
The present invention relates to a proportional difference pressure control valve which is improved on the basis of an original valve body, a valve core with a circular bead on the middle part, a ratio electromagnet, and a first main oil port, a second main oil port and a drainage port which are positioned on the valve body, namely that a left lower side passage is also arranged between a left passage and a transverse passage which is positioned on the left side of the circular bead, and a first throttle side and a second throttle side are respectively formed by the left side and the right side of the circular bead and transverse passage ports on the corresponding sides; when the ratio electromagnet is in a natural state, the first throttle side is in a normally opened state, and the second throttle side is in a normally closed state. After the structure is used, a variable damping hole corresponding to an electromagnet electrical signal is formed between the left side of the circular bead and the transverse passage port on the left side following the movement of the valve core in the transverse passage, and the hole diameter of the variable damping hole is larger than the hole diameter of a fixed damping hole. Therefore, a pass flow rate is increased under the same electromagnetism thrust force. Consequently, the present invention can be used for difference pressure control with a high flow rate or guide stage control to satisfy control requirements at different occasions.
Description
Technical field
The present invention relates to a kind of hydraulic control valve, especially refer to a kind of guide's control that is applicable to electro-hydraulic proportional flow valve or be directly used in the hydraulic system reduce pressure, to obtain the proportional differential pressure control valve of secondary pressure.
Background technique
In hydraulic transmission and control, be used for the ratio pressure Flow valve, proportional flow control valve, the pilot stage of proportion directional Flow valve, the general fixedly pilot controlled slide valve of damping hole of electro-hydraulic proportional reducing valve or band that adopts, as publication number is a kind of design proposal the Chinese invention patent application " pressure difference feedback type precontrolled slide valve " of CN1337539A has just disclosed, this control guiding valve comprises valve body, sliding spool, proportion electro-magnet and the first main hydraulic fluid port that is positioned on the valve body, second main hydraulic fluid port and the drain tap, be provided with the crosspassage of the horizontal arrangement that is complementary with described sliding spool in the valve body, described sliding spool is provided with a cylinder boss, this cylinder boss can move with described sliding spool, block or open the control port that forms between cylinder boss and valve body, one end of sliding spool contacts with the push rod of described proportion electro-magnet is concentric, the other end and spring offset, the place, left side of valve body is provided with and is communicated with the first main hydraulic fluid port and the horizontal left channel of left end all, the center of described valve body then is provided with an end and is connected with crosspassage, the vertical passage that the other end is connected with the second main hydraulic fluid port, between described left channel and described vertical passage, be provided with the damp channel of band damping hole, the upper end of described vertical passage is linked up mutually with the left end of the upper right side passage of described valve body, the right-hand member of described upper right side passage is linked up mutually with the right-hand member passage of described valve body, the right lower side of described valve body is provided with an end and is connected with drain tap, the right lower side passage that the crosspassage at the other end and cylinder boss right side place is linked up mutually.During work, because during hydraulic oil flow overdamping hole, the pressure reduction that produces between the first main hydraulic fluid port and the second main hydraulic fluid port can act on the two ends of sliding spool simultaneously, make sliding spool under the effect of electromagnetic push and pressure reduction, set up transient equiliblium, make control port have one and the corresponding opening degree of proportion electro-magnet electrical signal, thereby reach the purpose of hydraulic control.But find that in actual use when this control guiding valve was used for the occasion of big flow control, owing to be subjected to the restriction in damping hole aperture, its flow was less, can't satisfy the requirement of this big flow control; In addition, when its as one independently on-off valve carry out pressure reduction when control, the one-way cylinder that for example is used for the controlling combustion engine valve, equally, owing to be subjected to the restriction in damping hole aperture, make that the opening speed of oil cylinder piston is slower, resistance is big, so that must between the first main hydraulic fluid port and the second main hydraulic fluid port, add an Auxiliary valves, help piston as Pilot operated check valve and accelerate return speed, but so often make complex system and cost height, thereby in the time need being used for such occasion, above-mentioned pilot controlled slide valve need remain still further to be improved.
Summary of the invention
Technical problem to be solved by this invention is to provide the proportional differential pressure control valve that a kind of damping is variable and flow is big at the present situation of prior art
The present invention solves the problems of the technologies described above the technological scheme that is adopted: this proportional differential pressure control valve comprises valve body, the spool of middle part band shoulder, proportion electro-magnet and the first main hydraulic fluid port that is positioned on the valve body, second main hydraulic fluid port and the drain tap, be provided with the crosspassage of the horizontal arrangement that is complementary with described spool in the described valve body, the push rod of described spool right-hand member and described proportion electro-magnet offsets, place, described valve body left side is provided with and is communicated with the first above-mentioned main hydraulic fluid port and the left channel of crosspassage left end, the center of described valve body then is provided with an end and is connected with the described second main hydraulic fluid port, the vertical passage that the other end is connected with the crosspassage at shoulder place, and between described vertical passage and described crosspassage right-hand member, be provided with right channel, also being provided with an end on the described valve body is connected with drain tap, the right lower side passage that the other end and the crosspassage that is positioned at described shoulder right side place are linked up mutually, it is characterized in that: described left channel and be positioned between the crosspassage at place, described shoulder left side and also be provided with the lower-left side canal, and a described shoulder left side, right both sides respectively and form the first throttle limit and the second throttling limit between the crosspassage mouth of respective side, described proportion electro-magnet is under nature, described first throttle limit is a normally open, and the described second throttling limit is a normally off.
For in adjustment process, make electromagnet push rod and spool remain the state that touches mutually, in the crosspassage of described spool left end side, be provided with and make spool have spring all the time, to help improving dynamic response performance to electromagnet side shifting trend.
Described right channel can be positioned at the place, upper right side of valve body, and its left end is linked up mutually with the upper end of described vertical passage, and its right-hand member is linked up mutually with the right-hand member passage that is positioned at the valve body right side.
Compared with prior art, the invention has the advantages that: after adopting said structure, along with spool moving in crosspassage, formed one and the corresponding adaptive damping of electromagnet electrical signal hole between shoulder left side and the crosspassage mouth, and its aperture is far longer than the fixedly aperture of damping hole, therefore, under same electromagnetic push, the flow that flows through also just increases, thereby makes it can be used for the pressure reduction control or the pilot stage control of the big flow of needs, to satisfy the control needs of different occasions.
Description of drawings
Fig. 1 is the structural representation of embodiments of the invention;
Fig. 2 is the embodiment of the invention as the structural representation after pilot stage and the main valve configuration;
Fig. 3 is used for the structural representation of engine valve one-way cylinder control for the present invention.
Embodiment
Embodiment describes in further detail the present invention below in conjunction with accompanying drawing.
As shown in Figure 1, this proportional differential pressure control valve comprises valve body 1, the spool 2 of middle part band shoulder 21, proportion electro-magnet (not looking among the figure) and be positioned at the first main hydraulic fluid port A on the valve body 1, second main hydraulic fluid port B and the drain tap T, be provided with the crosspassage 11 of the horizontal arrangement that is complementary with spool 2 in the described valve body 1, the push rod 4 of spool 2 right-hand members and described proportion electro-magnet offsets, and an end of the left end of spool and a spring 3 offsets, the other end and the spring seat of spring 2 offset, and spring seat and valve body 1 are tightly connected, make spool 2 have trend all the time to the electromagnet side shifting, make in the course of the work simultaneously, the push rod of spool and electromagnet is in contacted state all the time, and make electromagnet have an initial current value, help improving dynamic performance.
Place, described valve body 1 left side is provided with and is communicated with the first above-mentioned main hydraulic fluid port A and the left channel 12 of crosspassage 11 left ends, the center of described valve body 1 then is provided with an end and is connected with the described second main hydraulic fluid port B, the vertical passage 14 that the other end is connected with the crosspassage 11 at shoulder place, and between vertical passage 14 and crosspassage 11 right-hand members, be provided with right channel 15, in the present embodiment, this right channel 15 is positioned at the place, upper right side of valve body 1, its left end is linked up mutually with the upper end of vertical passage 14, and its right-hand member is linked up mutually with the right-hand member passage 16 of described valve body, and described right-hand member passage 16 connects with crosspassage again; Also being provided with an end on the described valve body 1 is connected with drain tap T, the right lower side passage 17 that the other end and the crosspassage 11 that is positioned at described shoulder right side place are linked up mutually, left channel 12 and between the crosspassage 11 at shoulder left side place, then be provided with logical 13 roads of lower-left side, described shoulder 21 and arranged on left and right sides respectively and form the first throttle limit C1 and the second throttling limit C2 between 11 mouthfuls of the crosspassages of respective side, under the proportion electro-magnet nature, promptly do not have under the state of electrical signal, described first throttle limit C1 is a normally open, and the second throttling limit C2 is a normally off.
When this control valve uses as guide's controlled stage, as shown in Figure 2, it is on the 3BY2-G125B type ratio pressure flow combined valve 5 that this control valve is assemblied in model, be connected with valve body of main valve 51 by screw, make the first main hydraulic fluid port A of control valve be connected with the snout cavity C of main valve, the second main hydraulic fluid port B of control valve links to each other with the epicoele D of main valve, and the drain tap T of control valve communicates with the draining chamber L of main valve.
Its working principle is as follows: during beginning, when the electric current of proportion electro-magnet is zero, be the thrust F=0 of proportion electro-magnet, this moment is if control valve spool 2 is in opening state, the pressure that then draws the self-hydraulic system is to be divided into two tunnel, one road hydraulic oil acts on spool 2 by left channel 12 left end behind the first main hydraulic fluid port A of pressure oil through the oil suction chamber C of main valve, control valve of P; After another road hydraulic oil enters the crosspassage, first throttle limit C1, the second throttling limit C2, right lower side passage 17 at shoulder left side place successively by lower-left side canal 13, draining chamber L by drain tap T, main valve flows to fuel tank again, pressure oil is behind process first throttle limit C1, and pressure is reduced to P1 by P; This another road hydraulic oil is by the crosspassage at place, shoulder left side simultaneously, behind the first throttle limit, from the upper end of vertical passage 14 to right channel 15 and right-hand member passage 16, act on the right-hand member of spool 2 at last, it is vertical passage, be full of the hydraulic oil that pressure is P1 in right channel and the right-hand member passage, this pressure P 1 acts on the right-hand member of spool 2, pressure differential deltap P is applied to the two ends of spool 2 like this, making spool drive shoulder 21 moves right, until shoulder 21 the second throttling limit C2 is closed, hydraulic oil stops to flow, the pressure reduction of oil everywhere in the control valve is zero, control valve is in closed condition, and just main valve plug epicoele D oil pressure equates with oil pressure between the snout cavity C, and main valve 5 is under the effect of self spring 52 restoring force, close between the snout cavity C of main valve and the outlet plenum E, promptly main valve does not have flow output yet.
When proportion electro-magnet passes to certain electric current, produce the electromagnetic push F that is directly proportional with electric current, this electromagnetic push F overcomes the active force of spring 3, spool 2 is moved to the left, the second throttling limit C2 is opened, identical with above-mentioned principle, pressure is that the hydraulic oil part of P acts on the left end of spool by left channel 12, and another part pressure oil is after through first throttle limit C1, and pressure is reduced to pressure P 1 by P, if Δ P=P-P1, the snout cavity C of main valve plug and the pressure of epicoele D are respectively P and P1 at this moment, under the effect of Δ P, and compression main spool spring 52, main valve plug 53 is opened, and main valve promptly has flow output.This pressure is the right-hand member that the hydraulic oil of P1 acts on spool 2 simultaneously, be that pressure differential deltap P also is applied to the spool two ends simultaneously, produce active force to the right, overcome the ferreous F of electromagnetism, make spool 2 drive shoulder 21 and move right, the opening degree of the second throttling limit C2 reduces, control flow rate descends, Δ P also descends, and the oil pressure and the electromagnet thrust F of end balance each other until about spool 2, and spool reaches the corresponding transient equiliblium of the electrical signal with proportion electro-magnet.Obtain regime flow and pressure reduction this moment, also obtained stable pressure reduction between the first main hydraulic fluid port and the second main hydraulic fluid port.The opening degree of this pressure reduction may command main valve plug makes main valve output stable flow rate.
When the proportion electro-magnet electric current increases, electromagnetic push F overcome spool 2 about end pressure differential deltap P, making spool 2 drive shoulder 21 is moved to the left, the opening of the second throttling limit C2 is increased, then pressure is that the hydraulic oil of P also increases through the pressure differential deltap P behind the first throttle limit, promptly the pressure reduction between the first main hydraulic fluid port A and the second main hydraulic fluid port B also increases, and the snout cavity C of main valve plug and the pressure reduction between epicoele D are also increased, and finally causes snout cavity C to flow to the proportional increase of flow of outlet plenum E.Simultaneously this pressure differential deltap P affact spool 2 about end, promote spool 2 and move right, final and electromagnetic push F reaches till the transient equiliblium.
Otherwise, when the proportion electro-magnet electric current reduces, end pressure differential deltap P overcomes electromagnetic push about spool, spool 2 and shoulder 21 are moved right, the opening of the second throttling limit C2 is reduced, and then pressure is that the hydraulic oil of P also reduces through the pressure differential deltap P behind the first throttle limit C1, and promptly the pressure reduction between the first main hydraulic fluid port A and the second main hydraulic fluid port B also reduces, the snout cavity C of main valve and the pressure reduction between epicoele D also reduce, and make snout cavity C flow to proportional the reducing of flow of outlet plenum E.Simultaneously this pressure differential deltap P affact spool 2 about end, make spool 2 stop to move right, final and electromagnetic push F reaches till the transient equiliblium.
When this control valve is used for the control of engine valve one-way cylinder, as shown in Figure 3, then its first main hydraulic fluid port A, the second main hydraulic fluid port B link to each other with the left and right chamber of oil cylinder 6 by oil inlet pipe, oil outlet tube respectively, with in like manner above-mentioned, when on the second throttling limit C2, having flow to flow through, on the C1 of first throttle limit, will produce pressure reduction, this pressure reduction will be applied directly to the left chamber and the right chamber of oil hydraulic cylinder 6, increase if make a concerted effort, spring 7 then gradually reduces, piston 8 moves right, and drives valve head 9 by piston rod and moves right, and balances each other until the active force of making a concerted effort with spring 7; In like manner, if make a concerted effort to reduce, then under the effect of spring 7 restoring forces, piston 8 drives valve head 9 to left movement to left movement, also balances each other until the restoring force of making a concerted effort with spring 7; Under above-mentioned two states, piston 8 transfixions make to obtain a spacing correspondingly between valve head and the valve seat.
When the terminal point that moves to oil hydraulic cylinder 6 right-hand members when piston 8 needs left lateral, this moment, electromagnetic push F was zero, the flow that flows through control valve reduces to zero suddenly, Δ P=0 then, oil hydraulic cylinder 6 left sides, the oil pressure in right chamber equates, under the effect of spring 7 restoring forces, piston 8 quick left lateral, because control valve is in closed condition, this moment, the oil in piston 8 compressing oil hydraulic cylinders 6 left chambeies flowed to the second main hydraulic fluid port B from the first main hydraulic fluid port A, to produce pressure reduction at first throttle limit C1, this pressure reduction makes spool move to right by the two ends of channeling in spool, and then first throttle limit C1 increases, flow is unimpeded, valve returns rapidly, and therefore, need not to be provided with the return speed of accelerating valve as the Auxiliary valves of Pilot operated check valve and so on this moment between the left chamber of oil hydraulic cylinder 6 and chamber, the oil hydraulic cylinder right side, make system simpler, reliably, and still can reach the purpose of valve quick return.
Claims (3)
1, a kind of proportional differential pressure control valve, it comprises valve body (1), the spool (2) of middle part band shoulder (21), proportion electro-magnet and the first main hydraulic fluid port (A) that is positioned on the valve body (1), the second main hydraulic fluid port (B) and drain tap (T), be provided with the crosspassage (11) of the horizontal arrangement that is complementary with described spool (2) in the described valve body (1), the push rod (4) of described spool (2) right-hand member and described proportion electro-magnet offsets, place, described valve body (1) left side is provided with the left channel (12) that is communicated with the above-mentioned first main hydraulic fluid port (A) with crosspassage left end, the center of described valve body then is provided with an end and is connected with the described second main hydraulic fluid port (B), the vertical passage (14) that the other end is connected with the crosspassage at shoulder place, and between described vertical passage (14) and described crosspassage (11) right-hand member, be provided with right channel (15), also being provided with an end on the described valve body is connected with drain tap (T), the right lower side passage (17) that the other end and the crosspassage that is positioned at described shoulder right side place are linked up mutually, it is characterized in that: described left channel (12) and be positioned between the crosspassage at place, described shoulder left side and also be provided with lower-left side canal (13), and described shoulder (a 21) left side, right both sides form the first throttle limit (C1) and the second throttling limit (C2) respectively and between the crosspassage of respective side (11) mouth, described proportion electro-magnet is under nature, described first throttle limit (C1) is a normally open, and the described second throttling limit (C2) is a normally off.
2, proportional differential pressure control valve according to claim 1 is characterized in that being provided with in the crosspassage of described spool (2) left end side and makes spool have spring (3) to electromagnet side shifting trend all the time.
3, proportional differential pressure control valve according to claim 1 and 2, it is characterized in that described right channel (15) is positioned at the place, upper right side of valve body (1), its left end is linked up mutually with the upper end of described vertical passage (14), and its right-hand member is linked up mutually with the right-hand member passage (16) that is positioned at the valve body right side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2003101227851A CN1300499C (en) | 2003-12-25 | 2003-12-25 | Ratio pressure difference control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2003101227851A CN1300499C (en) | 2003-12-25 | 2003-12-25 | Ratio pressure difference control valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1554873A CN1554873A (en) | 2004-12-15 |
| CN1300499C true CN1300499C (en) | 2007-02-14 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2003101227851A Expired - Fee Related CN1300499C (en) | 2003-12-25 | 2003-12-25 | Ratio pressure difference control valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1300499C (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104343759B (en) * | 2013-07-23 | 2016-02-24 | 武汉机械股份有限公司 | pressure maintaining valve |
| CN107725878B (en) * | 2017-08-30 | 2019-10-22 | 武汉船用机械有限责任公司 | A kind of stop valve and valve group |
| CN111102376B (en) * | 2018-10-26 | 2021-08-20 | 宁波方太厨具有限公司 | Control valve for gas water heater and gas water heater |
| CN110410531A (en) * | 2019-07-18 | 2019-11-05 | 圣邦集团有限公司 | A kind of hydraulic multitandem valve |
| CN111664267A (en) * | 2020-06-16 | 2020-09-15 | 杭州依技设备成套工程有限公司 | Gas differential pressure automatic switching valve |
| CN112253820B (en) * | 2020-10-19 | 2022-04-01 | 中国核动力研究设计院 | Pilot valve for pilot safety valve and pilot safety valve |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85109329B (en) * | 1985-12-26 | 1988-07-20 | 庄凤龄 | Precursory overflow valve |
| JP2001074154A (en) * | 1999-09-07 | 2001-03-23 | Kayaba Ind Co Ltd | Proportional electromagnetic relief valve |
| CN1337539A (en) * | 2001-09-05 | 2002-02-27 | 宁波华液机器制造有限公司 | Pressure difference feedback type precontrolled slide valve |
-
2003
- 2003-12-25 CN CNB2003101227851A patent/CN1300499C/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85109329B (en) * | 1985-12-26 | 1988-07-20 | 庄凤龄 | Precursory overflow valve |
| JP2001074154A (en) * | 1999-09-07 | 2001-03-23 | Kayaba Ind Co Ltd | Proportional electromagnetic relief valve |
| CN1337539A (en) * | 2001-09-05 | 2002-02-27 | 宁波华液机器制造有限公司 | Pressure difference feedback type precontrolled slide valve |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1554873A (en) | 2004-12-15 |
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