CN103615572B - Prestretching-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve - Google Patents
Prestretching-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve Download PDFInfo
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- CN103615572B CN103615572B CN201310497666.8A CN201310497666A CN103615572B CN 103615572 B CN103615572 B CN 103615572B CN 201310497666 A CN201310497666 A CN 201310497666A CN 103615572 B CN103615572 B CN 103615572B
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/078—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted and linearly movable closure members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Magnetically Actuated Valves (AREA)
- Servomotors (AREA)
Abstract
Prestretching-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve, and coupling and cylindrical compression spring connecting linear electromechanical converter are all turned round by pressure in the two ends of 2D valve; Cylindrical compression spring is arranged between valve body and sliding wedge, and its pre compressed magnitude is slightly larger than valve core stroke; Spool end shoulder, between end cap and valve body, form left and right sensitive cavity; End shoulders respectively offers pressure hole, is communicated with P mouth by spool endoporus; On valve body inner bore wall, two ends respectively offer a diameter is semi-circular cross-section damping slot, and the two ends of each damping slot communicate with the sensitive cavity of closing on and T mouth respectively; Pressure hole on the shoulder of spool two ends is crossing with damping slot, forms two small opening areas, flowed friction half-bridge in series; The pressure of the sensitive cavity at two ends is controlled by the flowed friction half-bridge at two ends respectively.
Description
Technical field
The invention belongs to the electro-hydraulic proportional valve in Fluid-transmission and control field, particularly relate to a kind of electro-hydraulic proportion reversing valve.
Background technique
Electro-hydraulic servo control technology has organically combined the advantage of Fluid-transmission control technique and information electronic technology, is applied, and rakes in successfully at important national strategy army industrial fields such as Aero-Space, sophisticated weapons, iron and steel, power generations.But electrohydraulic control simultaneously also also exists contamination resistance difference, valve internal pressure loss large (7MPa), manufacture cost and maintenance cost high, the defects such as system energy consumption loss is large.Because many defects that electrohydraulic control exists, the fast-response that it is had cannot be able to widely use in general industry equipment.Simultaneously traditional electrohydraulic valve controls the requirement of the high quality control system that can not meet again required for 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 industrial control system actual demand electrohydraulic control technology.
For these reasons, there has been proposed electrohydraulic proportion technology.As the representative of electrohydraulic proportion technology, electro-hydraulic proportional valve is on the basis of traditional industry hydrovalve, adopts reliably inexpensive electromechanical converter (proportion electro-magnet etc.) and corresponding valve to design.Thus we just obtain to oil require identical with general industry valve, valve internal pressure loss is few, performance can meet again the proportional control element that most of industrial control requires.
Because electro-hydraulic proportional valve can be combined with electric control device, computing and process can be carried out to various input, output signal very easily, realize complicated controlling functions.It has again antipollution, low cost and responds advantage faster simultaneously.Obtain a wide range of applications in the industrial production, as ceramic floor brick pressure machine, the band steel constant tensile control being with steel to roll, 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 ratio control system, electro-hydraulic proportional valve is 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 successful part of the most significant characteristic sum of electro-hydraulic proportional valve is that adoption rate electromagnet is as electromechanical converter.Compare with 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 export larger power and displacement, and working service is convenient.Proportion electro-magnet, except being used as to drive pilot valve, also can be used as the low power output stage of Direct driver.Such as, balance each other and control the direct action type proportional valve of valve element position principle, be only applicable to small flow occasion according to electromagnet thrust and spring force, the maximum functional flow of practical application is generally 21MPa at 15L/min(maximum service pressure) below.In addition, in order to realize axial static pressure equilibrium of forces, direct action type proportional selector valve or Flow valve all adopt sliding valve structure, and " clamping stagnation " phenomenon appears in the impact being easily subject to frictional force and oil contamination.
Linear displacement transducer (LVDT) is adopted to measure and closed loop control valve element position, form electric feedback-type direct acting proportional reversing valve, locating stiffness and the control accuracy of spool can be improved to a great extent, simultaneously, people are also at its model, non-linear and system application aspect has carried out a large amount of theoretical research work, finally make electricity feedback direct acting Proportional valve can be applied to the closed loop control of hydraulic system as servovalve, but eventually because being subject to magnetic saturation restriction, proportion electro-magnet ouput force is limited, fundamentally cannot solve high pressure, under large discharge, hydraulic power affects problem, still flow saturated phenomenon is there will be under the working state of high pressure (pressure reduction is large) and large discharge.
Eliminate hydraulic power impact, improve the conveyance capacity of hydrovalve, the most basic way adopts to lead control (pilot control) technology.High pressure cannot be realized to solve because hydraulic power affects direct acting relief valve as far back as American engineer HarryVickers in 1936, the pressure control problems of Mass flow system invented and led control relief valve, its basic thought is that the pilot valve that employing one latus rectum is less controls static pressure, driving main valve plug moves, because when this hydraulic thrust flows through valve port than fluid, institute's hydraulic power that produces is much bigger, be enough to eliminate it to main valve plug motion and the adverse effect controlling to produce.The thought leading control was also widely used in the design of other hydrovalve afterwards, makes hydraulic system high pressure, large discharge is controlled in order to reality.Various electro-hydraulic servo control elements afterwards are also the design philosophys 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
There is " clamping stagnation " phenomenon to overcome being subject to the impact of frictional force, hydraulic power and oil contamination of existing electro-hydraulic proportional valve and lead control level oil circuit decompression or pressure is too low makes whole valve cannot normally work and lead the larger deficiency of control level leakage flow, the invention provides and a kind ofly not only have that common control type of leading electro-hydraulic proportional valve flow is large, working pressure high, and the prestretching-pretwist type that also can realize proportional control function under zero-pressure (decompression) as direct action type proportional valve simplifies full-bridge type 2D electro-hydraulic proportion reversing valve.
Prestretching of the present invention-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve, turns round coupling etc. form by the linear electromechanical converter 2,16 at 2D valve, two ends and the pressure be between them.
Prestretching-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve, comprise a 2D valve be made up of spool 9, valve body 8, spool 9 is rotatable also can be arranged in valve body 8 endoporus axially slidably, spool about 9 two ends are respectively provided with end shoulders, valve body 8 endoporus between described end shoulders has T mouth, A mouth, P mouth, B mouth, T mouth successively, wherein P mouth is liquid entering hole, and this place's pressure is system pressure; Between described end shoulders spool 9 be provided with two middle part shoulders, two 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:
Coupling and cylindrical compression spring 23,21 connecting linear electromechanical converter 2,16 are all turned round by pressure in the two ends of 2D valve;
Spool end shoulder, between end cap 4 and 19 and valve body 8, form left and right sensitive cavity (f and g);
Spool end shoulder respectively offers pressure hole (b, c), to be communicated with P mouth by spool endoporus k and hole a; On valve body inner bore wall two ends respectively offer a semi-circular cross-section damping slot (d and e), the sensitive cavity that each damping slot closes on it respectively and T mouth communicate;
Described pressure hole respectively has two on the shoulder of spool end, and the shaft axis mutually in spool is symmetrical; Described damping slot two ends on valve body inner bore wall respectively have two, and the shaft axis mutually in spool is symmetrical.
Pressure hole on the shoulder at spool two ends is crossing with damping slot, forms small opening area, flowed friction half-bridge in series; The pressure of the sensitive cavity at two ends is controlled by the flowed friction half-bridge at two ends respectively;
Pressure turn round coupling by sliding wedge 20, be fixed on two rolling bearings on bearing pin 18 end through spool end 14,38, the pin 10 and 22 that rotates of the linear bearing 13 and 32 be installed on sliding wedge, restriction sliding wedge forms; Cylindrical compression spring is arranged between valve body and sliding wedge, and its pre compressed magnitude is slightly larger than valve core stroke; Described sliding wedge is enclosed within slidably by linear bearing on the pin of the shaft axis being parallel to spool;
Described sliding wedge is provided with the first inclined-plane and second inclined-plane of the both sides laying respectively at described shaft axis, the first described inclined-plane and the second inclined-plane extend along two symmetry planes being parallel to described shaft axis are interior separately, the first described inclined-plane and the second inclined-plane are according to described shaft axis phase-inversion symmetric, two described rolling bearings roll respectively on the first inclined-plane and the second inclined-plane, so that spool twists when axial motion; The inclined-plane of the sliding wedge at two ends cooperatively interacts and makes the windup-degree of spool and spool have along the position of described shaft axis the corresponding relation determined.
Be positioned at inclined-plane on the sliding wedge at the two ends of described shaft axis homonymy respectively from the forward and back two sides of the sense of rotation of spool respectively against the bearing of the homonymy at described spool two ends.
It is the structure that the straight line motion realizing linear electromechanical converter transfers the twist motion of spool to that described pressure turns round coupling.In this process, the feature of 2D valve hydraulic pressure Dao Kongqiao road Pressure gain large (small corner can make the pressure of sensitive cavity that larger change occurs) can be made full use of, by turning round the appropriate design of coupling to pressure, by driving the torsional moment of valve core rotation to amplify, the adverse effect of the non-linear factor comparative example characteristics such as the frictional force between spool and spool bore is made to be reduced to minimum degree.
The electromagnetic push that linear electromechanical converter exports turns round coupling by pressure makes valve core rotation, and then the pressure of the valve sensitive cavity actuating valve core that changes is moved axially, in the process of movement, spool rotates backward, the pressure of its sensitive cavity reverts to original value again gradually, spool arrives a new equilibrium position, the displacement of spool movement and the proportional relation of the thrust of proportion electro-magnet.
Beneficial effect of the present invention is mainly manifested in: 1, for proportion electro-magnet because magnetic saturation thrust output is limited, propose pressure and turn round amplification actuation techniques, proportion electro-magnet is amplified the driving force of spool, effectively eliminates the adverse effect that the non-linear factor comparative example characteristics such as the 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 road delivery pressure is changed, and then produce the axial motion of static pressure actuating valve core, effectively can overcome the adverse effect that hydraulic power (Bernouilli force) causes under high pressure, large discharge, 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 that structure is simple, principle is advanced, not only have that common control type of leading electro-hydraulic proportional valve flow is large, working pressure high feature, and also can realize proportional control function as direct action type proportional valve under zero-pressure (decompression).4, relative 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 process a hole, and structure is simplified, and processing cost is reduced.
Accompanying drawing explanation
Fig. 1 is the structural representation that prestretching-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve.
Fig. 2 is the spool valve body assembling schematic diagram that prestretching-pretwist type simplifies 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 that spool and rolling bearing assemble 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 leads control full-bridge schematic diagram.
Figure 12-14 is that prestretching-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve force analysis and movement process figure.
Embodiment
Below in conjunction with accompanying drawing, the invention will be further described.
With reference to Fig. 1 ~ Figure 10, a kind of prestretching-pretwist type simplify full-bridge type 2D electro-hydraulic proportion reversing valve comprise 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, mark closely screw 34, steel ball 35, sleeve 37,39.
Prestretching-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve, turns round coupling etc. form by the linear electromechanical converter 2,16 at 2D valve, two ends and the pressure be between them.
Prestretching-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve, comprise a 2D valve be made up of spool 9, valve body 8, spool 9 is rotatable also can be arranged in valve body 8 endoporus axially slidably, spool about 9 two ends are respectively provided with end shoulders, valve body 8 endoporus between described end shoulders has T mouth, A mouth, P mouth, B mouth, T mouth successively, wherein P mouth is liquid entering hole, and this place's pressure is system pressure; Between described end shoulders spool be provided with two middle part shoulders, two 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:
Coupling and cylindrical compression spring 23,21 connecting linear electromechanical converter 2,16 are all turned round by pressure in the two ends of 2D valve;
Spool end shoulder, between end cap 4 and 19 and valve body 8, form left and right sensitive cavity (f and g);
As shown in Figure 3, Figure 4, spool end shoulder respectively offers pressure hole (b, c), to be communicated with P mouth by spool endoporus k and hole a;
As shown in Figure 5, Figure 6, on valve body inner bore wall two ends respectively offer a semi-circular cross-section damping slot (d and e), the sensitive cavity that each damping slot closes on it respectively and T mouth communicate;
Preferably, described damping slot is diametrically 0.5 ~ 1.0mm semi-circular cross-section.
Described pressure hole has two on the shoulder of spool end, and the shaft axis mutually in spool is symmetrical; Described damping slot two ends on valve body inner bore wall respectively have two, and the shaft axis mutually in spool is symmetrical.
As shown in figure 11, the pressure hole on the shoulder at spool two ends is crossing with damping slot, forms small opening area, flowed friction half-bridge in series; The pressure of the sensitive cavity at two ends is controlled by the flowed friction half-bridge at two ends respectively;
Pressure turn round coupling by sliding wedge 20, be fixed on two rolling bearings on bearing pin 18 end through spool end 14,38, be installed on sliding wedge hole p, the pin 10 and 22 that the linear bearing 13 and 32 in q hole, restriction sliding wedge rotate is formed; Cylindrical compression spring 21 is arranged between valve body 8 and sliding wedge 20, and its pre compressed magnitude is slightly larger than valve core stroke; Described sliding wedge is enclosed within slidably by linear bearing on the pin of the shaft axis being parallel to spool;
Described sliding wedge is provided with the first inclined-plane and second inclined-plane of the both sides laying respectively at described shaft axis, the first described inclined-plane and the second inclined-plane extend along two symmetry planes being parallel to described shaft axis are interior separately, the first described inclined-plane and the second inclined-plane are according to described shaft axis phase-inversion symmetric, two described rolling bearings roll respectively on the first inclined-plane and the second inclined-plane, so that spool twists when axial motion; The inclined-plane of the sliding wedge at two ends cooperatively interacts and makes the windup-degree of spool and spool have along the position of described shaft axis the corresponding relation determined.
Be positioned at inclined-plane on the sliding wedge at the two ends of described shaft axis homonymy respectively from the forward and back two sides of the sense of rotation of spool respectively against the bearing of the homonymy at described spool two ends.
It is the structure that the straight line motion realizing linear electromechanical converter transfers the twist motion of spool to that pressure turns round coupling.In this process, the feature of 2D valve hydraulic pressure Dao Kongqiao road Pressure gain large (small corner can make the pressure of sensitive cavity that larger change occurs) can be made full use of, by turning round the appropriate design of coupling to pressure, by driving the torsional moment of valve core rotation to amplify, the adverse effect of the non-linear factor comparative example characteristics such as the frictional force between spool and spool bore is made to be reduced to minimum degree.
Described O RunddichtringO 6,11 is used for sealing between end cap and valve body; Described O RunddichtringO 15,29 is used for sealing between end cap and linear electromechanical converter; The great circle styletable n of described top cover 17,28 is connected with the central bore interference fit of sliding wedge 20,25, and the masterpiece that the push rod of linear electromechanical converter exports 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 in sliding wedge upper and lower two holes p, q respectively symmetrically, in order to reduce frictional force when sliding wedge slides on pin; Described screw 34 of marking closely is used for steel ball 35 to withstand on an end face of spool endoporus k, is used for sealing one end of spool endoporus k; One end of described sleeve 37,39 withstands on spool, and the other end withstands on the inner ring of rolling bearing 36,38, 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
sthe position that (left end and right-hand member are represented by subscript " l " and " r " respectively) is contacted with two rolling bearings by two axisymmetric inclined-planes of sliding wedge is passed to spool.Due to the effect on inclined-plane, spool is except bearing axial tension F
soutward, also tangential force F is born
teffect, contrary with the tangential force equal and opposite in direction of two contact positions in one end, direction, form couple.The sliding wedge at two ends is contrary with couple direction to the axial force of spool, and thus when equilibrium position, spool is in the state of prestretching and pretwist.When the proportion electro-magnet energising of 2D electro-hydraulic proportional valve end, its thrust F produced
mnot only make the axial force disequilibrium of spool when acting on sliding wedge, and make the moment of torsion disequilibrium suffered by spool, valve core rotation.Such as when the proportion electro-magnet energising of left end, produce electromagnetic push F to the right
ml, the sliding wedge of left end is reduced, the axial force suffered by spool two ends and moment of torsion all disequilibriums to the active force of spool, spool is subject to axial driving force to the right and anticlockwise torque (seeing from left to right).Axial driving force is equivalent to the driving force of direct action type proportional valve, under the operating mode of high-pressure high-flow, due to exist hydraulic power and frictional force cannot Direct driver poppet shaft to motion.But, by reasonably selecting less sliding wedge bevel angle β and larger rolling bearing pitch circle diameter, larger tangential force can be obtained, its frictional force drives spool being enough to overcome spool is rotated counterclockwise.Meanwhile, the sliding wedge at two ends is owing to being subject to the circumference constraint of pin, be the axis of guide with pin, be that supporting is slided to the right with linear bearing, the decrement of right-hand member spring reduces, left end amount of spring compression increases, produce the thrust (see Figure 13) of extra spring force balanced proportions electromagnet.In this process, because spool rotates counterclockwise, the pressure of the left sensitive cavity of valve raises, the pressure of right sensitive cavity reduces, spool moves right, because the rolling bearing at its two ends is subject to the constraint on sliding wedge inclined-plane, two ends in movement process, spool while moving right also toward back rotation (rotating clockwise), 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 mouth of valve is zero (equal with T mouth pressure), now, cannot be moved axially by the change actuating valve core of two ends sensitive cavity pressure, but owing to flowing without fluid in valve pocket, spool is not subject to the effect of hydraulic power and clamping force, thus, the end thrust produced after proportion electro-magnet energising can be moved by Direct driver spool, and at this moment the working principle of 2D electro-hydraulic proportional valve is consistent with direct action type proportional valve.
Above-mentioned embodiment is used for explaining the present invention, instead of limits the invention, and in the protection domain of spirit of the present invention and claim, any amendment make the present invention and change, all fall into protection scope of the present invention.
Claims (3)
1. prestretching-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve, comprise a 2D valve be made up of spool, valve body, spool is rotatable also can be arranged in valve body inner bore axially slidably, two ends, spool left and right are respectively provided with end shoulders, valve body inner bore between described end shoulders has successively T mouth, A mouth, P mouth, B mouth, T mouth, wherein P mouth is liquid entering hole, and this place's pressure is system pressure; Between described end shoulders spool be provided with two middle part shoulders, two 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:
Coupling and cylindrical compression spring connecting linear electromechanical converter are all turned round by pressure in the two ends of 2D valve;
Spool end shoulder, between end cap and valve body, form left and right sensitive cavity (f and g);
Spool end shoulder respectively offers pressure hole (b, c), to be communicated with P mouth by spool endoporus; On valve body inner bore wall two ends respectively offer a semi-circular cross-section damping slot (d and e), the sensitive cavity that each damping slot closes on it respectively and T mouth communicate; Pressure hole on the shoulder at spool two ends is crossing with damping slot, forms small opening area, flowed friction half-bridge in series; The pressure of the sensitive cavity at two ends is controlled by the flowed friction half-bridge at two ends respectively;
Pressure turn round coupling by sliding wedge, be fixed on two rolling bearings at bearing pin two ends through spool end, pin that the linear bearing be installed on sliding wedge, restriction sliding wedge rotate forms; Cylindrical compression spring is arranged between valve body and sliding wedge, and its pre compressed magnitude is slightly larger than spool stroke; Described sliding wedge is enclosed within slidably by linear bearing on the pin of the shaft axis being parallel to spool;
Described sliding wedge is provided with the first inclined-plane and second inclined-plane of the both sides laying respectively at described shaft axis, the first described inclined-plane and the second inclined-plane extend along two symmetry planes being parallel to described shaft axis are interior separately, the first described inclined-plane and the second inclined-plane are according to described shaft axis phase-inversion symmetric, two described rolling bearings roll respectively on the first inclined-plane and the second inclined-plane, so that spool twists when axial motion; The inclined-plane of the sliding wedge at two ends cooperatively interacts and makes the windup-degree of spool and spool have along the position of described shaft axis the corresponding relation determined.
2. proportional reversing valve as claimed in claim 1, is characterized in that: be positioned at inclined-plane on the sliding wedge at the two ends of described shaft axis homonymy respectively from the forward and back two sides of the sense of rotation of spool respectively against the rolling bearing of the homonymy at described spool two ends.
3. proportional reversing valve as claimed in claim 1 or 2, is characterized in that: described pressure hole has two on the shoulder of spool end, and the shaft axis mutually in spool is symmetrical; Described damping slot respectively has two at valve body inner bore wall two ends, and the shaft axis mutually in spool is symmetrical.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310497666.8A CN103615572B (en) | 2013-04-27 | 2013-10-21 | Prestretching-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310158087.0 | 2013-04-27 | ||
| CN2013101580870A CN103277531A (en) | 2013-04-27 | 2013-04-27 | Pre-stretching-pre-twisting type simplified full-bridge 2D electro-hydraulic proportional reversing valve |
| CN201310497666.8A CN103615572B (en) | 2013-04-27 | 2013-10-21 | Prestretching-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve |
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| CN201310497666.8A Active CN103615572B (en) | 2013-04-27 | 2013-10-21 | Prestretching-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105465083A (en) * | 2016-01-25 | 2016-04-06 | 浙江大学城市学院 | Symmetrical full-bridge bi-directional 2D electro-hydraulic proportional reversing valve |
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| CN103256401A (en) * | 2013-04-27 | 2013-08-21 | 浙江工业大学 | Prestretching-pretwisting type full-bridge 2D electro-hydraulic proportional directional valve |
| CN103711945B (en) * | 2013-09-17 | 2016-03-09 | 浙江工业大学 | Monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve |
| CN104534124B (en) * | 2014-12-01 | 2017-01-18 | 浙江工业大学 | Displacement amplifying type 2D electro-hydraulic proportional directional valve |
| CN105465454B (en) * | 2016-01-25 | 2018-04-13 | 杭州博忆科技有限公司 | Two-way big flow type electro-hydraulic proportion reversing valve |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6585004B1 (en) * | 2002-01-17 | 2003-07-01 | Delaware Capital Formation, Inc. | Multi-stage flow control |
| CN101666341A (en) * | 2009-09-25 | 2010-03-10 | 浙江工业大学 | High frequency large flow 2D digital servo valve |
| CN101737371A (en) * | 2010-02-09 | 2010-06-16 | 浙江工业大学 | Zero maintaining mechanism of 2D digital servo valve |
| CN102168700A (en) * | 2011-05-06 | 2011-08-31 | 浙江工业大学 | Permanent magnet zero-position retaining mechanism of two-dimensional digital servo valve |
| CN102213243A (en) * | 2011-06-01 | 2011-10-12 | 武汉科技大学 | Composite high-efficiency high-flow servo valve |
| CN102913496A (en) * | 2012-10-24 | 2013-02-06 | 浙江工业大学 | Bi-directional full-bridge 2D electro-hydraulic proportional directional valve |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102008059013A1 (en) * | 2008-11-26 | 2010-05-27 | Schaeffler Kg | Electromagnetic actuator |
-
2013
- 2013-04-27 CN CN2013101580870A patent/CN103277531A/en active Pending
- 2013-10-21 CN CN201310497666.8A patent/CN103615572B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6585004B1 (en) * | 2002-01-17 | 2003-07-01 | Delaware Capital Formation, Inc. | Multi-stage flow control |
| CN101666341A (en) * | 2009-09-25 | 2010-03-10 | 浙江工业大学 | High frequency large flow 2D digital servo valve |
| CN101737371A (en) * | 2010-02-09 | 2010-06-16 | 浙江工业大学 | Zero maintaining mechanism of 2D digital servo valve |
| CN102168700A (en) * | 2011-05-06 | 2011-08-31 | 浙江工业大学 | Permanent magnet zero-position retaining mechanism of two-dimensional digital servo valve |
| CN102213243A (en) * | 2011-06-01 | 2011-10-12 | 武汉科技大学 | Composite high-efficiency high-flow servo valve |
| CN102913496A (en) * | 2012-10-24 | 2013-02-06 | 浙江工业大学 | Bi-directional full-bridge 2D electro-hydraulic proportional directional valve |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105465083A (en) * | 2016-01-25 | 2016-04-06 | 浙江大学城市学院 | Symmetrical full-bridge bi-directional 2D electro-hydraulic proportional reversing valve |
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| CN103615572A (en) | 2014-03-05 |
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