CN103711945B - Monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve - Google Patents
Monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve Download PDFInfo
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- CN103711945B CN103711945B CN201310424259.4A CN201310424259A CN103711945B CN 103711945 B CN103711945 B CN 103711945B CN 201310424259 A CN201310424259 A CN 201310424259A CN 103711945 B CN103711945 B CN 103711945B
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Classifications
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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
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F16K31/0603—Multiple-way valves
- F16K31/061—Sliding valves
- F16K31/0613—Sliding valves with cylindrical slides
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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
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
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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)
Abstract
Monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve, monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve is turned round coupling three part by 2D valve, linear electromechanical converter and pressure and is formed; Coupling and spring connecting linear electromechanical converter are turned round by pressure in one end of 2D valve; Spool end shoulder respectively offers a pair high and low pressure hole, first pressure hole b and the second pressure hole c is through hole, communicate with P mouth respectively by hole a and spool endoporus k, the first low pressure hole d, the second low pressure hole e communicate with T mouth respectively by the groove inside spool end shoulder; Two ends on valve body inner bore wall respectively offer a pair and axisymmetricly experience passage, communicate respectively with left and right sensitive cavity; Pressure hole on spool end shoulder, low pressure hole are crossing with one of described impression passage respectively, and form two small opening areas, flowed friction half-bridge in series, the pressure of two ends sensitive cavity 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 acquisition is identical with general industry valve to oil requirement, 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 and various engineering machinery 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, good manufacturability, the advantages such as larger power and displacement and working service is convenient can be exported.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 according to electromagnet thrust and spring force and control the direct action type proportional valve of valve element position principle, be only applicable to small flow occasion, the maximum functional flow of practical application is generally at 15 ~ below 40L/min.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.Its basic thought is that the less pilot valve of employing one latus rectum controls static pressure, drives main valve plug motion, because when this hydraulic thrust flows through valve port than fluid, institute's hydraulic power that produces is much bigger, is enough to eliminate it to main valve plug motion and the adverse effect controlling to produce.But it is more complicated to lead control valve arrangement, and the regular event of valve depends on and leads governor pressure, and cannot work under zero-pressure.
Summary of the invention:
In order to the large discharge that cannot realize by hydraulic power affects overcoming existing direct action type electrohydraulic proportional valve controls and the more complicated and too low deficiency making whole valve normally work of oil circuit decompression or pressure of pilot control structure, 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 under zero-pressure (decompression), also can realize the monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve of proportional control function as direct action type proportional valve.
Monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve is turned round coupling three part by 2D valve, linear electromechanical converter and pressure and is formed; The push rod of linear electromechanical converter is connected with the m end of right sliding wedge 15 by described coupling 13;
Described 2D valve portion comprises a spool 5 and a valve body 4, spool 5 is rotatable also can be arranged in valve body 4 endoporus axially slidably, spool about 5 two ends 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 5 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 spring connecting linear electromechanical converter are turned round by pressure in one end of 2D valve;
Spool end shoulder, between left end cap 2 and valve body 4, form left sensitive cavity h, spool end shoulder, between right end cap 10 and valve body 4, form right sensitive cavity j;
Spool end shoulder respectively offers a pair high and low pressure hole, the first pressure hole b, the first low pressure hole d and the second pressure hole c, the second low pressure hole e; First pressure hole b and the second pressure hole c is through hole, communicates with P mouth respectively by hole a and spool endoporus k, and the first low pressure hole d, the second low pressure hole e communicate with T mouth respectively by the groove inside spool end shoulder;
Two ends on valve body inner bore wall respectively offer a pair and axisymmetricly experience passage (f
1, f
2and g
1, g
2), communicate with left sensitive cavity h and right sensitive cavity j respectively;
Pressure hole on spool end shoulder, low pressure hole are crossing with one of described impression passage respectively, and form two small opening areas, flowed friction half-bridge in series, the pressure of two ends sensitive cavity is controlled by the flowed friction half-bridge at two ends respectively;
Described pressure is turned round coupling and is comprised left sliding wedge 16, right sliding wedge 15, is connected to the first rolling bearing 26, second rolling bearing 32 on the first horizontal bearing pin 33 of spool 5 end and the 3rd rolling bearing 28, the 4th rolling bearing 30 on the second horizontal bearing pin 31, and described sliding wedge is enclosed within slidably by linear bearing on the pin of the shaft axis being parallel to spool 5; Left sliding wedge is provided with the first inclined-plane and second inclined-plane of the both sides laying respectively at described shaft axis, right sliding wedge is provided with the 3rd inclined-plane and the 4th inclined-plane of the both sides laying respectively at described shaft axis, four described inclined-planes 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, and the 3rd described inclined-plane and the 4th inclined-plane are also according to described shaft axis phase-inversion symmetric; Described clutch shaft bearing and the second bearing roll respectively on the first inclined-plane and the second inclined-plane, and the 3rd described bearing and the 4th bearing roll respectively on the 3rd inclined-plane and the 4th inclined-plane, so that spool twists when axial motion; Left sliding wedge 16 and right sliding wedge 15 have the inclined-plane configuration mode making the windup-degree of spool 5 and spool 5 have the corresponding relation determined along the position of described shaft axis; First cylindrical compression spring 14 is arranged between right end cap and right sliding wedge, and the second cylindrical compression spring 17 is arranged between valve body and left sliding wedge, and the pre compressed magnitude of two springs is slightly larger than spool stroke.
Further, left sliding wedge 16 with the inclined-plane fit system of right sliding wedge 15 is: the inclined-plane on the described left sliding wedge 16 being positioned at described shaft axis homonymy and right sliding wedge 15 ramp respectively from the forward and back two sides of the sense of rotation of spool 5 respectively against the bearing of the homonymy of the first horizontal bearing pin 33 and the second rolling bearing 32.
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.
Basic functional principle of the present invention: the thrust that linear electromechanical converter exports or pulling force turn 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 ouput force 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 electro-hydraulic proportion reversing 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 selector valve, pressure are turned round coupling and the coaxial connection of proportion electro-magnet three, form monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing 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).
Accompanying drawing explanation
Fig. 1 is the structural representation of monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve.
Fig. 2 is the erection drawing of monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve.
Fig. 3 is the valve core structure schematic diagram of monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve.
Fig. 4 is the valve core inside structure sectional view of monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve.
Fig. 5 is monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve valve body sectional view.
Fig. 6 is the valve body side view of monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve.
Fig. 7 is monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve spool and rolling bearing assembly.
Fig. 8 is the inner side surface structural representation of right sliding wedge.
Fig. 9 is the formation outside schematic diagram of right sliding wedge.
Figure 10 is the inner side surface structural representation of left sliding wedge.
Figure 11 is the formation outside schematic diagram of left sliding wedge.
Figure 12 is that hydraulic pressure leads control full-bridge schematic diagram.。
Embodiment
Below in conjunction with accompanying drawing, the invention will be further described.
With reference to Fig. 1 ~ Figure 12, monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve comprise screw 1,7,20,23, left end cap 2, O RunddichtringO 3,11,18, valve body 4, spool 5, pin 6,19, linear bearing 8,9,21,22, right end cap 10, linear electromechanical converter 12, coupling 13, cylindrical compression spring 14,17, right sliding wedge 15, left sliding wedge 16, steel ball 24, mark closely screw 25, rolling bearing 26,28,30,32, sleeve 27,29, bearing pin 31,33.
Monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve is turned round coupling three part by 2D valve, linear electromechanical converter and pressure and is formed.
Described 2D valve portion comprises a spool 5 and a valve body 4, spool 5 is rotatable also can be arranged in valve body 4 endoporus axially slidably, spool about 5 two ends 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 5 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 spring connecting linear electromechanical converter are turned round by pressure in one end of 2D valve;
Spool end shoulder, between left end cap 2 and valve body 4, form left sensitive cavity h, spool end shoulder, between right end cap 10 and valve body 4, form right sensitive cavity j;
As shown in Figure 2, Figure 3, Figure 4, spool end shoulder respectively offers a pair high and low pressure hole (b, d and c, e).Wherein, pressure hole b, c are through hole, and communicate with P mouth respectively by hole a and spool endoporus k, low pressure hole d, e do not run through spool, are arranged on shoulder axisymmetrically, and communicate with T mouth respectively by the groove inside spool end shoulder;
As shown in Figure 5, Figure 6, the two ends on valve body inner bore wall respectively offer a pair axisymmetric impression passage (f
1, f
2and g
1, g
2), respectively with left and right sensitive cavity (h and j) to communicate;
As shown in figure 12, the high and low pressure hole on spool end shoulder with experience passages intersect, form two small opening areas, flowed friction half-bridge in series, the pressure of two ends sensitive cavity is controlled by the flowed friction half-bridge at two ends respectively.
Described pressure turns round that coupling comprises left sliding wedge 16, right sliding wedge 15, is connected to the first rolling bearing 26, second rolling bearing 32 on the first horizontal bearing pin 33 of spool 5 end and the 3rd rolling bearing 28 on the second horizontal bearing pin 31, the 4th rolling bearing 30, be installed on the hole p of left sliding wedge 16
2, q
2in linear bearing 8,22, be installed on the hole p of right sliding wedge 17
1, q
1interior linear bearing 9, 21, two described sliding wedges are enclosed within the pin 6 of the shaft axis being parallel to spool 5 slidably by four linear bearings, on 19, left sliding wedge is provided with the first inclined-plane and second inclined-plane of the both sides laying respectively at described shaft axis, right sliding wedge is provided with the 3rd inclined-plane and the 4th inclined-plane of the both sides laying respectively at described shaft axis, four described inclined-planes 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, the 3rd described inclined-plane and the 4th inclined-plane are also according to described shaft axis phase-inversion symmetric, described clutch shaft bearing and the second bearing roll respectively on the first inclined-plane and the second inclined-plane, and the 3rd described bearing and the 4th bearing roll respectively on the 3rd inclined-plane and the 4th inclined-plane, so that spool twists when axial motion, left sliding wedge 16 and right sliding wedge 15 have the inclined-plane configuration mode making the windup-degree of spool 5 and spool 5 have the corresponding relation determined along the position of described shaft axis, cylindrical compression spring 14 is arranged between right end cap and right sliding wedge, and cylindrical compression spring 17 is arranged between valve body and left sliding wedge, and the pre compressed magnitude of two springs is slightly larger than spool stroke.
Particularly, left sliding wedge 16 with the inclined-plane fit system of right sliding wedge 15 is: be positioned at inclined-plane on the left sliding wedge 16 of described shaft axis homonymy and right sliding wedge 15 ramp respectively from the forward and back two sides of the sense of rotation of spool 5 respectively against the bearing of the homonymy of the first horizontal bearing pin 33 and the second rolling bearing 32.The windup-degree of such spool 5 and spool 5 have along the position of described shaft axis the corresponding relation determined, the namely rotary motion of spool 5 and axial linear movement set up function relation.
Described O RunddichtringO 3,18 is used for sealing between left and right end cap and valve body; Described O RunddichtringO 11 is used for sealing between right end cap and linear electromechanical converter; Described coupling 13 is used for the push rod of linear electromechanical converter to be connected with the m end of right sliding wedge 15.Steel ball 24 withstands on an end face of spool endoporus k by described screw 25 of marking closely, and is used for sealing one end of spool endoporus k; One end of described sleeve 27,29 withstands on spool, and the other end withstands on the inner ring of rolling bearing 26,28, plays the effect of spring bearing.
Described high and low pressure hole shape is circular, if require that the axial motion of spool has capability of fast response to rotary motion, then can adopt the rectangular window of large size gradient.
Described linear electromechanical converter is the wet type high pressure-resistant proportion electro-magnet of double action (can thrust output can export pulling force again), also can select the linear electromechanical converter of wet type high pressure-resistant of other double action.
The working principle of the present embodiment: when proportion electro-magnet 12 no electric circuit, Compress Spring 14 is passed to spool to the position that right sliding wedge 15 thrust is left contacted with two rolling bearings by two axisymmetric inclined-planes of right sliding wedge.Due to the effect on inclined-plane, spool, except the end thrust of bearing left, also bears the effect of tangential force, and tangential force equal and opposite in direction, the direction of two contact positions are contrary, form counterclockwise couple (seeing from right to left).In like manner, Compress Spring 17 also creates an end thrust to the right and a clockwise couple to spool by left sliding wedge 16.Two sliding wedges are contrary with couple equal and opposite in direction direction to the axial force of spool, and thus when equilibrium position, spool is in the state of prestretching and pretwist.When proportion electro-magnet 12 is energized, when its thrust produced or pulling force act on right sliding wedge, not only make the axial force disequilibrium of spool, and make the moment of torsion disequilibrium suffered by spool, valve core rotation.Such as, when proportion electro-magnet energising produces electromagnetic push left, right sliding wedge increases the active force of spool, the axial force suffered by spool two ends and moment of torsion all disequilibriums, and spool is subject to axial driving force left and anticlockwise torque.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 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, two sliding wedges are owing to being subject to the circumference constraint of pin, and be the axis of guide with pin, be that supporting is slided left with linear bearing, the decrement of spring 14 reduces, spring 17 decrement increases, produce the thrust of extra spring force balanced proportions electromagnet.In this process, because spool rotates counterclockwise, the pressure of the left sensitive cavity h of valve reduces, the pressure of right sensitive cavity j raises, spool under the effect of hydraulic coupling to left movement, 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 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 (4)
1. monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve, monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve is turned round coupling three part by 2D valve, linear electromechanical converter and pressure and is formed; The axle head of the push rod of linear electromechanical converter with right sliding wedge (15) is connected by described coupling (13);
Described 2D valve portion comprises a spool (5) and a valve body (4), spool (5) is rotatable also can be arranged in valve body (4) endoporus axially slidably, spool (5) two ends, 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 (5) 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 spring connecting linear electromechanical converter are turned round by pressure in one end of 2D valve;
Spool end shoulder, between left end cap (2) and valve body (4), form left sensitive cavity (h), spool end shoulder, between right end cap (10) and valve body (4), form right sensitive cavity (j);
Spool end shoulder respectively offers a pair high and low pressure hole, the first pressure hole (b), the first low pressure hole (d) and the second pressure hole (c), the second low pressure hole (e); First pressure hole (b) and the second pressure hole (c) are through hole, communicate with P mouth respectively by hole (a) and spool endoporus (k), the first low pressure hole (d), the second low pressure hole (e) communicate with T mouth respectively by the groove inside spool end shoulder;
Two ends on valve body inner bore wall respectively offer a pair and axisymmetricly experience passage (f
1, f
2and g
1, g
2), communicate with left sensitive cavity (h) and right sensitive cavity (j) respectively;
Pressure hole on spool end shoulder, low pressure hole are crossing with one of described impression passage respectively, and form two small opening areas, flowed friction half-bridge in series, the pressure of two ends sensitive cavity is controlled by the flowed friction half-bridge at two ends respectively;
Described pressure is turned round coupling and is comprised the 3rd rolling bearing (28), the 4th rolling bearing (30) on left sliding wedge (16), right sliding wedge (15), the first rolling bearing (26) be connected on the first horizontal bearing pin (33) of spool (5) end, the second rolling bearing (32) and the second horizontal bearing pin (31), and described sliding wedge is enclosed within slidably by linear bearing on the pin of the shaft axis being parallel to spool (5); Left sliding wedge is provided with the first inclined-plane and second inclined-plane of the both sides laying respectively at described shaft axis, right sliding wedge is provided with the 3rd inclined-plane and the 4th inclined-plane of the both sides laying respectively at described shaft axis, four described inclined-planes 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, and the 3rd described inclined-plane and the 4th inclined-plane are also according to described shaft axis phase-inversion symmetric; Clutch shaft bearing and the second bearing roll respectively on the first inclined-plane and the second inclined-plane, and the 3rd bearing and the 4th bearing roll respectively on the 3rd inclined-plane and the 4th inclined-plane, so that spool twists when axial motion; Left sliding wedge (16) and right sliding wedge (15) have the inclined-plane configuration mode making the windup-degree of spool (5) and spool (5) have the corresponding relation determined along the position of described shaft axis; First cylindrical compression spring (14) is arranged between right end cap and right sliding wedge, and the second cylindrical compression spring (17) is arranged between valve body and left sliding wedge, and the pre compressed magnitude of two springs is slightly larger than spool stroke.
2. proportional reversing valve as claimed in claim 1, is characterized in that: be positioned at inclined-plane on the left sliding wedge (16) of described shaft axis homonymy and right sliding wedge (15) ramp respectively from the forward and back two sides of the sense of rotation of spool (5) respectively against the bearing of the homonymy of the first horizontal bearing pin (33) and the second rolling bearing (32).
3. proportional reversing valve as claimed in claim 1, is characterized in that: one end of sleeve (27,29) withstands on spool, with spring bearing on the inner ring that the other end withstands on rolling bearing (26,28).
4. proportional reversing valve as claimed in claim 1, is characterized in that: described high and low pressure hole adopts the rectangular window of large size gradient so that the axial motion of spool has capability of fast response to rotary motion.
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| CN201310424259.4A CN103711945B (en) | 2013-09-17 | 2013-09-17 | Monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve |
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| CN201310424259.4A CN103711945B (en) | 2013-09-17 | 2013-09-17 | Monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve |
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| CN103711945B true CN103711945B (en) | 2016-03-09 |
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| TWI601900B (en) * | 2016-06-16 | 2017-10-11 | Piezoelectric controlled pilot operated valve |
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