CN103615572A - Pre-tensioning - pre-twisting type simplified full-bridge 2D electro-hydraulic proportional directional valve - Google Patents
Pre-tensioning - pre-twisting type simplified full-bridge 2D electro-hydraulic proportional directional valve Download PDFInfo
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- CN103615572A CN103615572A CN201310497666.8A CN201310497666A CN103615572A CN 103615572 A CN103615572 A CN 103615572A CN 201310497666 A CN201310497666 A CN 201310497666A CN 103615572 A CN103615572 A CN 103615572A
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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
Abstract
Provided is a pre-tensioning - pre-twisting type simplified full-bridge 2D electro-hydraulic proportional directional valve. The two ends of the 2D valve are both connected with linear electro-mechanical converters through pressure-torsion couplings and cylindrical compression springs. The cylindrical compression springs are mounted between a valve body and sliding wedges, and the precompression amount is slightly larger than a valve core stroke. A left sensitive cavity and a right sensitive cavity are formed between end portion circular beads and end covers of a valve core and the valve body. The end portion circular beads are respectively provided with a high-pressure hole which is communicated with a P opening through a valve core inner hole. The two ends of the wall of a valve body inner hole are respectively provided with a dampening slot with the diameter being a semicircular cross section, and the two ends of each dampening slot are communicated with the adjacent sensitive cavities and T openings respectively. The high-pressure holes in the circular beads at the two ends of the valve core intersect with the dampening slots to form two tiny openings and are in series connection with the dampening slots to form hydraulic resistance half-bridges. The pressure of the sensitive cavities at the two ends is controlled by the hydraulic resistance half-bridges at the two ends respectively.
Description
Technical field
The invention belongs to the electro-hydraulic proportional valve in Fluid-transmission and control field, relate in particular 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 it is poor that electrohydraulic control also exists contamination resistance simultaneously, valve internal pressure loss large (7MPa), manufacture cost and maintenance cost are high, and system energy consumption loses the defects such as large.Because many defects that electrohydraulic control exists can cannot be widely used its fast-response having in general industry equipment.Simultaneously traditional electrohydraulic valve is controlled can not meet the requirement that modern industry is produced needed high quality control system again.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 have been required to proportional control element identical with general industry valve, that 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 to various inputs, output signal, carry out computing and processing very easily, realize complicated control function.It has again antipollution, low cost and responds advantage faster simultaneously.In industrial production, obtain a wide range of applications, as ceramic floor brick pressure machine, the permanent tension force control of band 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 the control system of rolling with steel, 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 significant feature of electro-hydraulic proportional valve and the most successful part are 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 be exported larger power and displacement, and working service is convenient.Proportion electro-magnet, except as driving pilot valve, also can be used as directly driving low power output stage.Such as, according to electromagnet thrust and spring force, balance each other 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 21MPa at 15L/min(maximum service pressure) below.In addition, in order to realize axial static, press 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 that is easily 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 as servovalve, be applied to the closed loop control of hydraulic system, but eventually because being subject to limitation of magnetic saturation, proportion electro-magnet ouput force is limited, cannot fundamentally solve high pressure, the problem that affects of hydraulic power under large flow, under the working state of high pressure (pressure reduction is large) and large flow, still there will be flow saturated phenomenon.
The conveyance capacity of eliminating 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, in order to solve the pressure control problem that cannot realize high pressure, Mass flow system because of the straight moving relief valve of hydraulic power impact, invented and led control relief valve, its basic thought is to adopt the pilot valve that a latus rectum is less to control static pressure, the motion of driving main valve plug, while flowing through valve port because of this hydraulic thrust 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 of controlling generation.The thought of leading control was also 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 are afterwards 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
In order to overcome being subject to frictional force, hydraulic power and oil contamination impact of existing electro-hydraulic proportional valve, there is " clamping stagnation " phenomenon and lead control level oil circuit decompression or pressure is too low makes whole valve cannot work and lead the larger deficiency of control level leakage flow, the invention provides and a kind ofly not only have that the common control type of leading electro-hydraulic proportional valve flow is large, working pressure high, and prestretching-pretwist type that also can realize proportional control function under zero-pressure (decompression) as direct action type proportional valve is simplified full-bridge type 2D electro-hydraulic proportion reversing valve.
Prestretching-pretwist type of the present invention is simplified full-bridge type 2D electro-hydraulic proportion reversing valve, by the linear electromechanical converter 2,16 at 2D valve, two ends with turn round coupling etc. in the pressure between them and form.
Prestretching-pretwist type is simplified full-bridge type 2D electro-hydraulic proportion reversing valve, comprise a 2D valve being formed by spool 9, 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 are respectively provided with end shoulders, on valve body 8 endoporus between described end shoulders, have 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 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:
The two ends of 2D valve are all turned round coupling by pressure and are connected linear electromechanical converter 2,16 with cylindrical compression spring 23,21;
Spool end shoulders, end cap 4 and 19 and valve body 8 between form left and right sensitive cavity (f and g);
On spool end shoulders, respectively offer pressure hole (b, c), by spool endoporus k and hole a, communicate with P mouth; On valve body inner bore wall, two ends respectively offer the damping slot (d and e) of a semi-circular cross-section, and 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 that is mutually spool is symmetrical; Described damping slot two ends on valve body inner bore wall respectively have two, and the shaft axis that is mutually spool is symmetrical.
Pressure hole on the shoulder at spool two ends and damping slot intersect, and form small opening area, flowed friction half-bridge in series; The pressure of the sensitive cavity at two ends is controlled by respectively the flowed friction half-bridge at two ends;
Pressure turn round coupling by sliding wedge 20, be fixed on one through two rolling bearings 14,38 on bearing pin 18 ends of spool end, be installed on the linear bearing 13 and 32 on sliding wedge, the pin 10 and 22 that restriction sliding wedge rotates 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 on the pin of the shaft axis that is parallel to spool slidably by linear bearing;
Described sliding wedge is provided with the first inclined-plane and second inclined-plane of the both sides that lay respectively at described shaft axis, the first described inclined-plane and the second inclined-plane extend along two symmetry planes that are 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 definite corresponding relation along the position of described shaft axis.
Be positioned at inclined-plane on the sliding wedge at 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 of realizing linear electromechanical converter transfers the twist motion of spool to that described pressure is turned round coupling.In this process, can make full use of the feature of 2D valve hydraulic pressure Dao Kongqiao road Pressure gain large (small corner can make the pressure of sensitive cavity that larger variation occurs), by pressure being turned round to the appropriate design of coupling, by driving the torsional moment of valve core rotation to amplify, make the adverse effect of the non-linear factor comparative example 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 the makes valve sensitive cavity actuating valve core that changes moves axially, in mobile process, spool rotates backward, 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.
Beneficial effect of the present invention is mainly manifested in: 1, for proportion electro-magnet because of magnetic saturation thrust output limited, proposed to press and turned round amplification actuation techniques, proportion electro-magnet is amplified the driving force of spool, effectively eliminated the adverse effect that the non-linear factor comparative example characteristics such as frictional force between spool and spool bore cause; 2, with the rotation of spool and two freedom of movement of slip, realize and lead control type electric-hydraulic proportion commutation (throttling) valve function, by valve core rotation, flowed friction bridge road delivery pressure is changed, and then generation static pressure actuating valve core axial motion, under high pressure, large flow, can effectively overcome the adverse effect that hydraulic power (Bernouilli force) causes, effectively improve axially locating (main valve opening) precision of spool; 3,2D commutation (throttling) valve, pressure are turned round to coupling and the coaxial connection of proportion electro-magnet three, form 2D electric-hydraulic proportion commutation (throttling) valve simple in structure, principle is advanced, not only have that the common control type of leading electro-hydraulic proportional valve flow is large, the high feature of working pressure, and also can as direct action type proportional valve, realize proportional control function 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.
Accompanying drawing explanation
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 invention will be 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 is simplified full-bridge type 2D electro-hydraulic proportion reversing valve, by the linear electromechanical converter 2,16 at 2D valve, two ends with turn round coupling etc. in the pressure between them and form.
Prestretching-pretwist type is simplified full-bridge type 2D electro-hydraulic proportion reversing valve, comprise a 2D valve being formed by spool 9, 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 are respectively provided with end shoulders, on valve body 8 endoporus between described end shoulders, have 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:
The two ends of 2D valve are all turned round coupling by pressure and are connected linear electromechanical converter 2,16 with cylindrical compression spring 23,21;
Spool end shoulders, end cap 4 and 19 and valve body 8 between form left and right sensitive cavity (f and g);
As shown in Figure 3, Figure 4, on spool end shoulders, respectively offer pressure hole (b, c), by spool endoporus k and hole a, communicate with P mouth;
As shown in Figure 5, Figure 6, on valve body inner bore wall, two ends respectively offer the damping slot (d and e) of a semi-circular cross-section, and the sensitive cavity that each damping slot closes on it respectively and T mouth communicate;
Preferably, to be diameter be 0.5～1.0mm semi-circular cross-section to described damping slot.
Described pressure hole has two on the shoulder of spool end, and the shaft axis that is mutually spool is symmetrical; Described damping slot two ends on valve body inner bore wall respectively have two, and the shaft axis that is mutually spool is symmetrical.
As shown in figure 11, the pressure hole on the shoulder at spool two ends and damping slot intersect, and form small opening area, flowed friction half-bridge in series; The pressure of the sensitive cavity at two ends is controlled by respectively the flowed friction half-bridge at two ends;
Pressure turn round coupling by sliding wedge 20, be fixed on one through two rolling bearings 14,38 on bearing pin 18 ends of spool end, 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 forms; 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 on the pin of the shaft axis that is parallel to spool slidably by linear bearing;
Described sliding wedge is provided with the first inclined-plane and second inclined-plane of the both sides that lay respectively at described shaft axis, the first described inclined-plane and the second inclined-plane extend along two symmetry planes that are 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 definite corresponding relation along the position of described shaft axis.
Be positioned at inclined-plane on the sliding wedge at 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 of realizing linear electromechanical converter transfers the twist motion of spool to that pressure is turned round coupling.In this process, can make full use of the feature of 2D valve hydraulic pressure Dao Kongqiao road Pressure gain large (small corner can make the pressure of sensitive cavity that larger variation occurs), by pressure being turned round to the appropriate design of coupling, by driving the torsional moment of valve core rotation to amplify, make the adverse effect of the non-linear factor comparative example 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; 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 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 sliding wedge upper and lower two hole p, q symmetrically, the frictional force while sliding on pin in order to reduce sliding wedge; The 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 one end of spool endoporus k to seal; 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
s(left end and right-hand member are represented by subscript " l " and " r " respectively) two axisymmetric inclined-planes by sliding wedge are passed to spool with the position that two rolling bearings contact.Due to the effect on inclined-plane, spool is except bearing axial tension F
salso bear tangential force F outward,
teffect, with tangential force equal and opposite in direction, the opposite direction of two contact positions in one end, form couple.The sliding wedge at two ends is to the axial force of spool and couple opposite direction, thereby when equilibrium position, the state of spool in prestretching and pretwist.When the proportion electro-magnet of 2D electro-hydraulic proportional valve end is switched on, the thrust F of its generation
mwhile acting on sliding wedge, not only make the axial force disequilibrium of spool, 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 of left end is reduced the active force of spool, the axial force that 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, owing to there being the directly actuating valve core axial motion of hydraulic power and frictional force.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 owing to being subject to the circumferential constraint of pin, the pin of take slides to the right as supporting as the axis of guide, the linear bearing of take, and the decrement of right-hand member spring reduces, 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 (equating with T mouth pressure), now, cannot move axially by the variation 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, thereby, the end thrust producing after 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 direct action type proportional valve.
Above-mentioned embodiment is used for explaining the present invention, rather than limits the invention, and in the protection domain of spirit of the present invention and claim, any modification and change that the present invention is made, all fall into protection scope of the present invention.
Claims (3)
1. prestretching-pretwist type is simplified full-bridge type 2D electro-hydraulic proportion reversing valve, comprise a 2D valve being 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 are respectively provided with end shoulders, in valve body inner bore between described end shoulders, have 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:
The two ends of 2D valve are all turned round coupling by pressure and are connected linear electromechanical converter with cylindrical compression spring;
Between spool end shoulders, end cap and valve body, form left and right sensitive cavity (f and g);
On spool end shoulders, respectively offer pressure hole (b, c), by spool endoporus, communicate with P mouth; On valve body inner bore wall, two ends respectively offer the damping slot (d and e) of a semi-circular cross-section, and the sensitive cavity that each damping slot closes on it respectively and T mouth communicate; Pressure hole on the shoulder at spool two ends and damping slot intersect, and form small opening area, flowed friction half-bridge in series; The pressure of the sensitive cavity at two ends is controlled by respectively the flowed friction half-bridge at two ends;
Pressure turn round coupling by sliding wedge, be fixed on two rolling bearings through the bearing pin two ends of spool end, be installed on the linear bearing on sliding wedge, the pin that restriction sliding wedge rotates 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 on the pin of the shaft axis that is parallel to spool slidably by linear bearing;
Described sliding wedge is provided with the first inclined-plane and second inclined-plane of the both sides that lay respectively at described shaft axis, the first described inclined-plane and the second inclined-plane extend along two symmetry planes that are 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 definite corresponding relation along the position of described shaft axis.
2. proportional reversing valve as claimed in claim 1, is characterized in that: be positioned at inclined-plane on the sliding wedge at 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.
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 that is mutually spool is symmetrical; Described damping slot respectively has two at valve body inner bore wall two ends, and the shaft axis that is mutually spool is symmetrical.
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| Application Number | Priority Date | Filing Date | Title |
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| 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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| Application Number | Priority Date | Filing Date | Title |
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| 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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| CN103615572B CN103615572B (en) | 2015-12-30 |
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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 (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104534124A (en) * | 2014-12-01 | 2015-04-22 | 浙江工业大学 | Displacement amplifying type 2D electro-hydraulic proportional directional valve |
| CN105465454A (en) * | 2016-01-25 | 2016-04-06 | 杭州博忆科技有限公司 | Bidirectional large-flow electro-hydraulic proportional reversing valve |
| CN105465086A (en) * | 2016-01-25 | 2016-04-06 | 浙江大学城市学院 | Force feedback type electro-hydraulic proportional directional valve for mollisol shield tunneling machine |
| CN105465084A (en) * | 2016-01-25 | 2016-04-06 | 浙江工业职业技术学院 | Full-bridge force feedback elastic compression-torsion coupler type 2D electro-hydraulic proportional directional valve |
| CN105465085A (en) * | 2016-01-25 | 2016-04-06 | 浙江大学城市学院 | Displacement reduction type 2D electro-hydraulic proportional reversing valve with compression-torsion couplers |
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| CN105465085A (en) * | 2016-01-25 | 2016-04-06 | 浙江大学城市学院 | Displacement reduction type 2D electro-hydraulic proportional reversing valve with compression-torsion couplers |
| CN105465085B (en) * | 2016-01-25 | 2017-09-01 | 浙江大学城市学院 | Displacement reduces formula pressure and turns round coupling type 2D electro-hydraulic proportion reversing valves |
| 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 |
| CN109578355A (en) * | 2018-11-12 | 2019-04-05 | 温州大学苍南研究院 | A kind of full-bridge type pilot control switch valve |
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| CN103277531A (en) | 2013-09-04 |
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