CN203286051U - Pretensioning-pretwisting type simplified full-bridge 2D electro-hydraulic proportional directional valve - Google Patents
Pretensioning-pretwisting type simplified full-bridge 2D electro-hydraulic proportional directional valve Download PDFInfo
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- CN203286051U CN203286051U CN2013202315825U CN201320231582U CN203286051U CN 203286051 U CN203286051 U CN 203286051U CN 2013202315825 U CN2013202315825 U CN 2013202315825U CN 201320231582 U CN201320231582 U CN 201320231582U CN 203286051 U CN203286051 U CN 203286051U
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Abstract
Disclosed is a pretensioning-pretwisting type simplified full-bridge 2D electro-hydraulic proportional directional valve. The two ends of a 2D valve are connected with a linear electric-mechanical convertor through a compressing-and-twisting coupler and a spring. One spring (4) is installed between a valve body and each sliding wedge, and the amount of pre-compression is slightly larger than the valve core stroke. A left sensitivity cavity is formed among one end portion shoulder, one sliding wedge and the valve body, and a right sensitivity cavity are formed among the other end portion shoulder, the other sliding wedge and the valve body. The end portion shoulders are provided with high pressure holes which are communicated with a P port through a valve core inner hole. The two ends of an inner hole wall of the valve body are respectively provided with a damping groove with the diameter being a semi-circular cross section. The two ends of each damping groove are communicated with the left sensitivity cavity, the right sensitivity cavity and a T port respectively. The high pressure holes in the shoulders at the two ends of a valve core are crossed with the damping grooves to form two tiny opening areas and are connected in series to form hydraulic resistance half-bridges. The pressure of the sensitivity cavities at the two ends is controlled by the hydraulic resistance half-bridges at the two ends.
Description
Technical field
The utility model belongs to the electro-hydraulic proportional valve in Fluid-transmission and control field, relates in particular to a kind of electro-hydraulic proportion reversing valve.
Background technique
The electro-hydraulic servo control technology has organically combined the advantage of Fluid-transmission control technique and information electronic technology, and the national strategy army industry field important at Aero-Space, sophisticated weapons, iron and steel, power generation etc. is applied, and rakes in successfully.It is poor that but electrohydraulic control also exists contamination resistance simultaneously, valve internal pressure loss large (7MPa), and manufacture cost and maintenance cost are high, and system energy consumption loses the defects such as large.Because many defects that electrohydraulic control exists, make its fast-response that has can't be widely used in general industry equipment.Simultaneously traditional electrohydraulic valve is controlled the requirement that can not meet again the needed high quality control system of modern industry production.Therefore, people wish a kind of production and maintenance cost is low, safe and reliable, control accuracy and response characteristic all can meet the electrohydraulic control technology of industrial control system actual demand.
For these reasons, people have proposed electrohydraulic proportion technology.As the representative of electrohydraulic proportion technology, electro-hydraulic proportional valve is to use on the basis of hydrovalve in traditional industry, adopts reliable inexpensive electromechanical converter (proportion electro-magnet etc.) and valve correspondingly to design.Thereby we have just obtained oil is required proportional control element identical with the general industry valve, that the valve internal pressure loss is few, performance can meet again most of industrial control requirement.
Because electro-hydraulic proportional valve can be combined with electric control device, can carry out computing and processing to various inputs, output signal very easily, realize complicated control function.It has again antipollution, low cost and responds advantage faster simultaneously.Obtain a wide range of applications permanent tension force controls of the band steel that rolls as ceramic floor brick pressure machine, with steel, pressurized container fatigue life test machine, hudraulic lift motion and control system, the control of metal-cutting machine tool working table movement, rolling mill pressure and control system, Presseshydraulic, tube bender, plastic injection machine etc. in industrial production.
In ratio control system, electro-hydraulic proportional valve is the electro-hydraulic conversion element, is also power amplification element simultaneously.It plays an important role to the performance of system, is the core parts of ratio control system.
The most significant feature of electro-hydraulic proportional valve and the most successful part are that the adoption rate electromagnet is as electromechanical converter.Compare with the moving-iron type torque motor with moving coil, proportion electro-magnet has simple and reliable for structure, and materials are general, and good manufacturability can be exported larger power and displacement, and working service is convenient.Proportion electro-magnet, except as driving pilot valve, also can be used as the low power output stage of direct driving.Such as, balance each other and control the direct action type proportional valve of valve element position principle according to electromagnet thrust and spring force, be only applicable to the small flow occasion, the maximum functional flow of practical application is generally 21MPa at the 15L/min(maximum service pressure) below.In addition, in order to realize the balance of axial static pressure, direct action type proportional selector valve or Flow valve all adopt sliding valve structure, and " clamping stagnation " phenomenon appears in the impact that easily is subject to frictional force and oil contamination.
adopt Linear displacement transducer (LVDT) to measure and closed loop control valve element position, form directly moving proportional reversing valve of electric feedback-type, can improve to a great extent locating stiffness and the control accuracy of spool, simultaneously, people are also at its model, a large amount of theoretical research work has been carried out in non-linear and system applies aspect, finally make the straight moving Proportional valve of electricity feedback can be applied to the closed loop control of hydraulic system as servovalve, but eventually because being subject to limitation of magnetic saturation, the proportion electro-magnet ouput force is limited, can't fundamentally solve high pressure, the problem that affects of hydraulic power under large flow, still there will be the flow saturated phenomenon under the working state of high pressure (pressure reduction is large) and large flow.
Eliminate the conveyance capacity of hydraulic power impact, raising hydrovalve, the most basic way is to adopt control (pilot control) technology of leading.As far back as American engineer Harry Vickers in 1936 for solve because of the straight moving relief valve of hydraulic power impact can't realize high pressure, Mass flow system pressure control problem model utility lead the control relief valve, its basic thought is to adopt the less pilot valve of a latus rectum to control static pressure, the motion of driving main valve plug, while because of this hydraulic thrust, than fluid, flowing through valve port, institute's hydraulic power that produces is much bigger, is enough to eliminate it to main valve plug motion and the adverse effect of controlling generation.The thought of leading control also was widely used in the design of other hydrovalve afterwards, made hydraulic system high pressure, large flow control become reality.Various electro-hydraulic servo control elements afterwards are also the design philosophys of having continued to use pilot control, and electro-hydraulic proportional valve is no exception, and have used the many structural principles of servovalve.
Summary of the invention
" clamping stagnation " phenomenon occurs in order to overcome being subject to frictional force, hydraulic power and oil contamination impact of existing electro-hydraulic proportional valve and lead control level oil circuit decompression or pressure is too low makes whole valve can't work and lead the larger deficiency of control level leakage flow, the utility model provides a kind of and has not only that the common control type of leading electro-hydraulic proportional valve flow is large, the working pressure high, and can realize as the direct action type proportional valve also that under zero-pressure (decompression) prestretching of proportional control function-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve.
Prestretching described in the utility model-pretwist type is simplified full-bridge type 2D electro-hydraulic proportion reversing valve, by the linear electromechanical converter 2 at 2D valve, two ends, 16 and be in pressure between them and turn round coupling etc. and form.The 2D valve mainly is comprised of spool 9 and valve body 8, and spool has rotation and two freedom of movement that slide (so gain the name " 2D valve ") in valve body.Respectively offer a pressure hole (b and c) on the shoulder of spool two ends, communicate with the P mouth respectively; Two ends respectively offer a pair of damping slot (d on the valve body inner bore wall
1, d
2And e
1, e
2), communicate with left and right sensitive cavity (f and g) and T mouth respectively.When spool is installed in spool bore, the pressure hole on the shoulder of spool two ends and damping slot intersect, and form two small opening areas, and series connection forms the flowed friction half-bridge.The pressure of two ends sensitive cavity is controlled by respectively the flowed friction half-bridge at two ends.
It is to realize that the straight line motion of linear electromechanical converter transfers the structure of the twist motion of spool to that described pressure is turned round coupling.In this process, can take full advantage of 2D valve hydraulic pressure and lead the characteristics of control bridge circuit Pressure gain large (small corner can make the pressure of sensitive cavity that larger variation occurs), by pressure being turned round the appropriate design of coupling, the torsional moment that drives valve core rotation is amplified, make the adverse effect of the non-linear factor Comparative Examples characteristics such as frictional force between spool and spool bore be reduced to minimum degree.
The electromagnetic push of linear electromechanical converter output is turned round coupling by pressure makes valve core rotation, and then the pressure that makes the valve sensitive cavity changes the actuating valve mandrel to movement, spool backward rotation in mobile process, the pressure of its sensitive cavity reverts to again original value gradually, spool arrives a new equilibrium position, the displacement that spool moves and the proportional relation of the thrust of proportion electro-magnet.
The beneficial effects of the utility model are mainly manifested in: 1, limited because of the magnetic saturation thrust output for proportion electro-magnet, proposed to press and turned round the amplification actuation techniques, proportion electro-magnet is amplified the driving force of spool, effectively eliminated the adverse effect that the non-linear factor Comparative Examples characteristics such as frictional force between spool and spool bore cause; 2, realize leading control type electric-hydraulic proportion commutation (throttling) valve function with the rotation of spool and two freedom of movement of slip, by valve core rotation, flowed friction bridge circuit delivery pressure is changed, and then produce static pressure actuating valve mandrel to motion, can effectively overcome the adverse effect that hydraulic power (Bernouilli force) causes under high pressure, large flow, effectively improve axially locating (main valve opening) precision of spool; 3,2D commutation (throttling) valve, pressure are turned round coupling and the coaxial connection of proportion electro-magnet three, form 2D electric-hydraulic proportion commutation (throttling) valve simple in structure, that principle is advanced, have not only that the common control type of leading electro-hydraulic proportional valve flow is large, the high characteristics of working pressure, and also can realize the proportional control function as the direct action type proportional valve under zero-pressure (decompression).4, with respect to the spool of prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve, the spool left and right shoulder of this valve only need be processed a hole, and structure is simplified, and processing cost is reduced.
Description of drawings
Fig. 1 is the structural representation that prestretching-pretwist type is simplified full-bridge type 2D electro-hydraulic proportion reversing valve.
Fig. 2 is the spool valve body assembling schematic diagram that prestretching-pretwist type is simplified full-bridge type 2D electro-hydraulic proportion reversing valve.
Fig. 3 is the structural representation of spool.
Fig. 4 is valve core inside structure sectional view.
Fig. 5 is the sectional view of valve body.
Fig. 6 is the side schematic view of valve body.
Fig. 7 is spool and rolling bearing assembling schematic diagram.
Fig. 8 is the structural representation of top cover.
Fig. 9 is the outer side surface structural representation of sliding wedge.
Figure 10 is the inner side surface structural representation of sliding wedge.
Figure 11 hydraulic pressure is led control full-bridge schematic diagram.
Figure 12-14 are that prestretching-pretwist type is simplified full-bridge type 2D electro-hydraulic proportion reversing valve force analysis and movement process figure.
Embodiment
Below in conjunction with accompanying drawing, the utility model is further described.
With reference to Fig. 1～Figure 10, a kind of prestretching-pretwist type is simplified full-bridge type 2D electro-hydraulic proportion reversing valve and is comprised screw 1,3,12,30,33, linear electromechanical converter 2,16, end cap 4,19, linear bearing 5,13,31,32, cylindrical compression spring 21,23, O RunddichtringO 6,11,15,29, pin 7,10,22,24, valve body 8, spool 9, rolling bearing 14,27,36,38, top cover 17,28, bearing pin 18,26, sliding wedge 20,25, marks closely screw 34, steel ball 35, sleeve 37,39.
Prestretching-pretwist type simplification full-bridge type 2D electro-hydraulic proportion reversing valve is turned round coupling three parts by 2D valve, linear electromechanical converter and pressure and is formed.
Described 2D valve portion comprises a spool 9 and a valve body 8, spool 9 is rotatable also can be arranged in valve body 8 endoporus axially slidably, spool 9 two ends, left and right respectively are provided with end shoulders, have successively T mouth, A mouth, P mouth, B mouth, T mouth on valve body inner bore between described end shoulders, wherein the P mouth is liquid entering hole, and this place's pressure is system pressure; Between described end shoulders spool 9 be provided with two the middle part shoulders, two the middle part shoulders lay respectively at A mouth and B mouth; Each shoulder and valve body inner bore are sealed and matched slidably; It is characterized in that:
The two ends of 2D valve are all turned round coupling by pressure and are connected linear electromechanical converter with spring;
Spool end shoulders, end cap 4,19 and valve body 8 between form left and right sensitive cavity f, g;
As shown in Figure 3, Figure 4, respectively offer pressure hole b, a c on the spool end shoulders, pressure hole b, c are through hole, communicate with the P mouth by hole a and spool endoporus k respectively;
As shown in Figure 5, Figure 6, the two ends on the valve body inner bore wall respectively offer the damping slot (d of a pair of axisymmetric semi-circular cross-section
1, d
2And e
1, e
2), the two ends of each damping slot communicate with left and right sensitive cavity (f and g) and T mouth respectively;
Preferably, to be diameter be 0.5～1.0mm semi-circular cross-section to described damping slot.
As shown in figure 11, the pressure hole on the spool end shoulders and damping slot intersect, and form two small opening areas, and series connection forms the flowed friction half-bridge, and the pressure of two ends sensitive cavity is controlled by respectively the flowed friction half-bridge at two ends.
Described pressure turn round coupling by sliding wedge 20, be fixed on one on bearing pin 18 ends of passing the spool end two rolling bearings 14,38, be installed on the linear bearing 13,32 in sliding wedge hole p, q, the pin 10,22 that the restriction sliding wedge rotates forms; Cylindrical compression spring 21 is arranged between valve body and sliding wedge, and its pre compressed magnitude is slightly larger than spool stroke;
It is to realize that the straight line motion of linear electromechanical converter transfers the structure of the twist motion of spool to that pressure is turned round coupling.In this process, can take full advantage of 2D valve hydraulic pressure and lead the characteristics of control bridge circuit Pressure gain large (small corner can make the pressure of sensitive cavity that larger variation occurs), by pressure being turned round the appropriate design of coupling, the torsional moment that drives valve core rotation is amplified, make the adverse effect of the non-linear factor Comparative Examples characteristics such as frictional force between spool and spool bore be reduced to minimum degree.
Described O RunddichtringO 6,11 is used for to sealing between end cap and valve body; Described O RunddichtringO 15,29 is used for to sealing between end cap and linear electromechanical converter; Described top cover 17,28 great circle styletable n and sliding wedge 20,25 central inner hole interference fit are connected, and the masterpiece of the push rod output of linear electromechanical converter is used on the roundlet styletable m of top cover, and transfers is to sliding wedge.Described linear bearing 5,31 and 13,32 is arranged on respectively in two of up and down of sliding wedge hole p, q symmetrically, the frictional force while in order to reduce sliding wedge, sliding on pin; The described screw 34 of marking closely is used for steel ball 35 is withstood on the end face of spool endoporus k, is used for the end of spool endoporus k is sealed; Described sleeve 37, an end of 39 withstand on spool, and the other end withstands on rolling bearing 36,38 inner ring, plays the effect of spring bearing.
Described linear electromechanical converter is wet type high pressure-resistant proportion electro-magnet, also can select the linear electromechanical converter of other wet type high pressure-resistant.
The working principle of the present embodiment: as shown in figure 12, when the proportion electro-magnet no electric circuit at 2D electro-hydraulic proportional valve two ends, spring produces outside thrust F to sliding wedge
S(left end and right-hand member are respectively by subscript " l " and " r " expression) is passed to spool by two axisymmetric inclined-planes and two contacted positions of rolling bearing of sliding wedge.Due to the effect on inclined-plane, spool is except bearing axial tension F
SAlso bear tangential force F outward,
tEffect, tangential force equal and opposite in direction, the opposite direction of two contact positions of same end, form couple.Axial force and the couple opposite direction of the sliding wedge at two ends to spool, thereby when equilibrium position, spool is in the state of prestretching and pretwist.When the proportion electro-magnet of 2D electro-hydraulic proportional valve end is switched on, the thrust F of its generation
mNot only make the axial force disequilibrium of spool while acting on sliding wedge, and make the suffered moment of torsion disequilibrium of spool, valve core rotation.For example when the proportion electro-magnet of left end is switched on, produce electromagnetic push F to the right
ml, the sliding wedge that makes left end reduces the active force of spool, and the axial force that the spool two ends are suffered and moment of torsion be disequilibrium all, and spool is subject to axial driving force and anticlockwise torque (seeing from left to right) to the right.Axial driving force is equivalent to the driving force of direct action type proportional valve, under the operating mode of the large flow of high pressure, due to exist hydraulic power and frictional force directly the actuating valve mandrel to motion.But,, by reasonably selecting less sliding wedge bevel angle β and larger rolling bearing distribution circular diameter, can obtain larger tangential force, its frictional force drives spool that is enough to overcome spool is rotated counterclockwise.Meanwhile, the sliding wedge at two ends is due to the circumferential constraint that is subject to pin, the slip to the right take pin as the axis of guide, take linear bearing as supporting, the decrement of right-hand member spring reduces, the left end amount of spring compression increases, the thrust (seeing Figure 13) of the extra spring force balanced proportions electromagnet that produces.In this process, because spool rotates counterclockwise, the pressure of the left sensitive cavity of valve raises, the pressure decreased of right sensitive cavity, spool moves right, and is subject to the constraint on sliding wedge inclined-plane, two ends in movement process due to the rolling bearing at its two ends, spool when moving right also toward back rotation (clockwise rotating), the pressure of spool two ends sensitive cavity reverts to the equilibrium value of stable state again, and spool arrives a new equilibrium position (see Figure 14) corresponding with proportion electro-magnet thrust size.It needs to be noted, when the pressure of the P of valve mouth is zero (with the T mouth pressure, equating), at this moment, can't pass through the variation actuating valve mandrel of two ends sensitive cavity pressure to movement, but owing to flowing without fluid in valve pocket, spool is not subjected to the effect of hydraulic power and clamping force, thereby, the end thrust that produces after the proportion electro-magnet energising can directly drive valve core movement, and at this moment the working principle of 2D electro-hydraulic proportional valve is consistent with the direct action type proportional valve.
Above-mentioned embodiment is used for explaining the utility model; rather than the utility model is limited; in the protection domain of spirit of the present utility model and claim, any modification and change to the utility model is made, all fall into protection domain of the present utility model.
Claims (3)
1. prestretching-pretwist type is simplified full-bridge type 2D electro-hydraulic proportion reversing valve, comprise a 2D valve that is formed by spool, valve body, spool is rotatable also can be arranged in valve body inner bore axially slidably, two ends, spool left and right respectively are provided with end shoulders, have successively T mouth, A mouth, P mouth, B mouth, T mouth on valve body inner bore between described end shoulders, wherein the P mouth is liquid entering hole, and this place's pressure is system pressure; Between described end shoulders spool be provided with two the middle part shoulders, two the middle part shoulders lay respectively at A mouth and B mouth; Each shoulder and valve body inner bore are sealed and matched slidably; It is characterized in that:
The two ends of 2D valve are all turned round coupling by pressure and are connected linear electromechanical converter with spring;
Pressure turn round coupling by sliding wedge (10), be fixed on one on bearing pin (13) end of passing the spool end two rolling bearings (9), be installed on the linear bearing (3) on sliding wedge, the pin (8) that the restriction sliding wedge rotates forms; Spring (4) is arranged between valve body and sliding wedge, and its pre compressed magnitude is slightly larger than the valve core stroke;
Form left and right sensitive cavity between end shoulders, sliding wedge (10) and valve body;
Respectively offer pressure hole (a, c) on end shoulders, by the spool endoporus, with the P mouth, communicate; Respectively to offer a diameter be semi-circular cross-section damping slot (b and d) at two ends on the valve body inner bore wall, and the two ends of each damping slot communicate with left and right sensitive cavity (e and f) and T mouth respectively; Pressure hole on the shoulder of spool two ends and damping slot intersect, and form two small opening areas, and series connection forms the flowed friction half-bridge; The pressure of the sensitive cavity at two ends is controlled by respectively the flowed friction half-bridge at two ends.
2. 2D electro-hydraulic proportion reversing valve as claimed in claim 1, it is characterized in that: described linear electromechanical converter is proportion electro-magnet.
3. 2D electro-hydraulic proportion reversing valve as claimed in claim 2, it is characterized in that: it is 0.5～1.0mm semi-circular cross-section that described damping slot is diameter.
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| Application Number | Priority Date | Filing Date | Title |
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| CN2013202315825U CN203286051U (en) | 2013-04-27 | 2013-04-27 | Pretensioning-pretwisting type simplified full-bridge 2D electro-hydraulic proportional directional valve |
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|---|---|---|---|
| CN2013202315825U CN203286051U (en) | 2013-04-27 | 2013-04-27 | Pretensioning-pretwisting type simplified full-bridge 2D electro-hydraulic proportional directional valve |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107289191A (en) * | 2017-07-18 | 2017-10-24 | 中国航空工业集团公司西安飞行自动控制研究所 | A kind of valve core structure of adjustable output gain |
-
2013
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107289191A (en) * | 2017-07-18 | 2017-10-24 | 中国航空工业集团公司西安飞行自动控制研究所 | A kind of valve core structure of adjustable output gain |
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Granted publication date: 20131113 Termination date: 20170427 |
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