CN113107918B - Two-dimensional half-bridge electrohydraulic proportional reversing valve based on gap compensation displacement amplification coupling - Google Patents

Two-dimensional half-bridge electrohydraulic proportional reversing valve based on gap compensation displacement amplification coupling Download PDF

Info

Publication number
CN113107918B
CN113107918B CN202110433316.XA CN202110433316A CN113107918B CN 113107918 B CN113107918 B CN 113107918B CN 202110433316 A CN202110433316 A CN 202110433316A CN 113107918 B CN113107918 B CN 113107918B
Authority
CN
China
Prior art keywords
valve
inclined wing
valve core
pressure
wing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN202110433316.XA
Other languages
Chinese (zh)
Other versions
CN113107918A (en
Inventor
孟彬
杨冠政
徐豪
朱晨航
戴铭柱
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zhejiang University of Technology ZJUT
Original Assignee
Zhejiang University of Technology ZJUT
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zhejiang University of Technology ZJUT filed Critical Zhejiang University of Technology ZJUT
Priority to CN202110433316.XA priority Critical patent/CN113107918B/en
Publication of CN113107918A publication Critical patent/CN113107918A/en
Application granted granted Critical
Publication of CN113107918B publication Critical patent/CN113107918B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • F15B13/021—Valves for interconnecting the fluid chambers of an actuator
    • 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

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

The two-dimensional half-bridge electro-hydraulic proportional reversing valve based on the gap compensation displacement amplification coupling comprises a bidirectional proportional electromagnet, a gap compensation type magnetic suspension displacement amplification coupling and a two-dimensional half-bridge electro-hydraulic proportional reversing valve body which are sequentially arranged from left to right; the two-dimensional half-bridge electro-hydraulic proportional reversing valve body comprises a valve core, a valve sleeve and a valve body, wherein the valve core is embedded in the valve sleeve, the valve sleeve is embedded in the valve body, and the valve core is connected with a two-way proportional electromagnet through a gap compensation type magnetic suspension displacement amplifying coupling; the gap compensation type magnetic suspension displacement amplification coupling comprises a magnetic suspension inclined wing assembly and a displacement amplification assembly; the inner inclined wing rotor is suspended between the upper inclined wing magnetic sheet and the lower inclined wing magnetic sheet by magnetic force, and can rotate for a certain angle. The invention fundamentally avoids the influence of inherent friction and abrasion, gaps and other static characteristics of the mechanical compression-torsion coupling on the linearity, symmetry and the like of the valve, and the displacement amplification technology can convert small displacement output by the proportional electromagnet into displacement of the valve core and amplify the displacement according to the proportion, thereby solving the adverse influence on the dynamic response characteristic of the electro-hydraulic proportional reversing valve caused by low frequency response and slow starting of the proportional electromagnet.

Description

Two-dimensional half-bridge electrohydraulic proportional reversing valve based on gap compensation displacement amplification coupling
Technical Field
The invention relates to a reversing control valve for electro-hydraulic proportional control technology in the field of fluid transmission and control, in particular to a two-dimensional half-bridge electro-hydraulic proportional reversing valve based on a gap compensation displacement amplification coupling.
Background
With the development of control theory, automatic control has penetrated into various fields of industrial technology, and has been increasingly widely applied in the mechanical manufacturing industry, particularly, the automatic control technology is applied to hydraulic transmission, the combination of the hydraulic technology and the microelectronic technology is realized, and the power as large as possible is transferred in the smallest space as possible and is precisely controlled. At present, the hydraulic technology has made great progress in various aspects of realizing high efficiency, high speed, high pressure, high integration, high power, low noise, intellectualization and the like, is widely applied to industrial occasions such as military weapons, marine vessels, steel smelting, aerospace and the like, and particularly in the last decades, and due to the development of the whole industrial technology, mainly the development of military weapons and aerospace technology, the hydraulic technology is promoted to be gradually perfected and matured in the aspects of elements and systems, and the hydraulic technology has become one of standards for measuring the degree of industrial development of a country.
Electrohydraulic servo control technology is an emerging scientific technology combining hydraulic technology and microelectronic technology, and since the forty of the last century, the electrohydraulic servo control technology has been particularly valued by the advantages of large power-weight ratio, quick response, high precision and the like, so that the electrohydraulic servo control technology occupies an important position in electromechanical transmission and control technology. In the early fifty years, along with the development of electromagnetic technology, a quick-response permanent magnet torque motor and a force motor appear, the generation and development of a quick electro-hydraulic servo control system are promoted, and in the last fifty years, an electro-hydraulic servo valve such as a nozzle-baffle valve and a jet pipe valve appears, and the quick response of the servo valve is further improved. In the beginning of sixties, electrohydraulic servo valves with various structures appear successively, the performance is also becoming perfect, electrohydraulic servo control technology has become an important aspect of industrial automation and weapon automation, and all control systems needing high power, quick and accurate reaction have electrohydraulic servo valves, such as the electrohydraulic servo valves are mainly applied to artillery, tank operating systems and missile automatic control systems in the national defense industry; in general industry, the method is mainly applied to the fields of machine tools, production lines, engineering machinery, construction machinery, ships and the like. Although the electrohydraulic servo valve has the advantages of quick response, high control precision and the like, the electrohydraulic servo valve is extremely sensitive to the pollution of oil, and has high requirements on the machining and assembling precision of parts, so that the manufacturing cost of the electrohydraulic servo valve is greatly increased, and a technology which has low machining and manufacturing cost, simple structure, reliable performance, strong pollution resistance, response characteristic and control precision and meets the actual requirement of a control system is generally expected to be provided, and the electrohydraulic proportional technology is developed under the background.
The electrohydraulic proportional control technology is a bridge connecting modern electronic technology and hydraulic technology, has become an important component of the basic technology of modern control engineering, and the key control element of the electrohydraulic proportional technology is an electrohydraulic proportional valve which mainly consists of a proportional electromagnet and a universal hydraulic valve. The performance of the electro-hydraulic proportional valve is between that of the switch type electromagnetic valve and the electro-hydraulic servo valve, and the valve can continuously and proportionally control parameters such as pressure, flow and the like of oil according to the input electric signals, and since seventies of the last century, the electro-hydraulic proportional valve starts to develop rapidly, and has the advantages of reliability, energy conservation, low cost and the like, and is widely applied to occasions with low requirements on dynamic performance in the technical field of industry. The electro-hydraulic servo valve has the most outstanding advantages that the pollution resistance is strong, the cleanliness standard of hydraulic oil required by the electro-hydraulic servo valve is required to reach Nas-3 level, the electro-hydraulic proportional valve is required to reach Nas-5 level, and the electro-hydraulic servo valve has simple structure, low processing and manufacturing precision requirements and relatively low price. In the modern industry, almost all pressure valves, flow valves and direction valves can find corresponding electro-hydraulic proportional products, and the electro-hydraulic proportional valves are increasingly widely applied in the industry field due to the remarkable advantages of the electro-hydraulic proportional valves.
The electro-hydraulic proportional directional valve mainly refers to an electro-hydraulic proportional reversing valve, and the valve is generally provided with three or more than three passage ports, so that the direction of liquid flow can be controlled, and the output flow can be controlled. The pilot valve and the main valve of the traditional electro-hydraulic proportional reversing valve are both four-side slide valves, wherein the pilot stage of the valve is a direct-acting proportional pressure reducing valve controlled in a two-way mode, so that the traditional electro-hydraulic proportional reversing valve is large in size and high in manufacturing cost, meanwhile, the response speed of the proportional reversing valve is reduced due to the existence of the proportional pressure reducing valve, and the pilot proportional reversing valve cannot work under zero pilot pressure. The direct-acting proportional directional valve can operate under zero pilot pressure, but the pilot stage structure of the electro-hydraulic proportional directional valve is innovated because the limit of the stroke of the proportional electromagnet cannot be adapted to the occasion of large flow. The teaching of the university of Zhejiang industry Ruan Jian proposes a 2D valve based on double degrees of freedom of a valve core, the valve integrates a pilot stage and a power stage, is integrated on a single valve core, reduces the volume of an electro-hydraulic proportional reversing valve, has quick dynamic response, and greatly improves the pollution resistance. However, the electro-hydraulic proportional reversing valve has a plurality of defects, firstly, the 2D valve is connected with the proportional electromagnet into a whole through a torque-pressing coupling, and the torque-pressing coupling consists of a roller inclined plane, and the static characteristics such as linearity, symmetry and the like of the electro-hydraulic proportional valve are seriously affected due to the influence of factors such as friction, assembly gaps and the like between the roller and the inclined plane; and secondly, the valve core travel of the 2D electro-hydraulic proportional reversing valve is limited by the travel of the proportional electromagnet, and the large-travel proportional electromagnet has the advantages of high manufacturing difficulty, low frequency response and slow starting, so that the dynamic response characteristic of the electro-hydraulic proportional reversing valve is greatly influenced.
The roller and the inclined plane of the traditional roller type displacement amplification coupling are in direct contact, a gap is required to exist in the displacement amplification part, if the gap is not available or is too small, the roller is blocked, the torque compression coupling cannot work normally, and therefore the gap becomes the largest factor of nonlinear generation of the displacement amplification coupling.
Disclosure of Invention
In order to solve the problem that friction and assembly errors exist between the roller and the inclined plane of the traditional mechanical compression torsion coupling and influence the linearity and symmetry of the roller and the inclined plane, and simultaneously, in order to reduce the influence of low frequency response of a proportional electromagnet and slow starting on the response speed of an electro-hydraulic proportional reversing valve, the invention further provides a two-dimensional half-bridge electro-hydraulic proportional reversing valve based on the gap compensation displacement amplification coupling, which is used for avoiding the phenomenon that the conventional roller type displacement amplification coupling is blocked due to no gap or too small gap.
The technical scheme adopted by the invention is as follows: the two-dimensional half-bridge electro-hydraulic proportional reversing valve based on the gap compensation displacement amplification coupling comprises a bidirectional proportional electromagnet (1), a gap compensation type magnetic suspension displacement amplification coupling and a two-dimensional half-bridge electro-hydraulic proportional reversing valve body which are sequentially arranged from left to right; the two-dimensional half-bridge electro-hydraulic proportional reversing valve body comprises a valve core (9), a valve sleeve (10) and a valve body (11), wherein the valve core (9) is embedded in the valve sleeve (10), the valve sleeve (10) is embedded in the valve body (11), and the valve core (9) is connected with the bidirectional proportional electromagnet (1) through a gap compensation type magnetic suspension displacement amplification coupling;
the gap compensation type magnetic suspension displacement amplification coupling comprises a magnetic suspension inclined wing assembly and a displacement amplification assembly; the magnetic suspension inclined wing assembly comprises an outer inclined wing rotor (4), an upper inclined wing magnetic sheet (5), a lower inclined wing magnetic sheet (16), an I-shaped magnetic sheet (17) and an inner inclined wing rotor (18); the inclined wing surfaces on both sides of the outer inclined wing rotor (4) and the inner inclined wing rotor (18) form a certain inclination angle with the horizontal plane, and are all characterized by 180-degree array taking the axis of the valve core (9) as a central axis; each side inclined wing surface of the outer inclined wing rotor (4) comprises an upper inclined wing surface and a lower inclined wing surface which are arranged up and down, a groove is formed in one side of each upper inclined wing surface and one side of each lower inclined wing surface, which are close to each other, and an upper inclined wing magnetic sheet (5) and a lower inclined wing magnetic sheet (16) are respectively embedded in the two grooves; the two side inclined wing surfaces of the inner inclined wing rotor (18) are pincerlike surfaces, and I-shaped magnetic sheets (17) are embedded in the pincerlike surfaces, so that the inner inclined wing rotor (18) is suspended between the upper inclined wing magnetic sheet (5) and the lower inclined wing magnetic sheet (16) by magnetic force; two working air gaps h with the same height are formed between the upper surface of the I-shaped magnetic sheet (17) and the upper oblique wing magnetic sheet (5) and between the lower surface of the I-shaped magnetic sheet (17) and the lower oblique wing magnetic sheet (16), and the inner oblique wing rotor (18) can rotate;
the displacement amplifying assembly comprises a supporting frame (6), rollers (23), roller supports (24), wedge blocks (29), a clearance compensation spring (30), a guide rail (31) and a linear bearing (32); the two roller supports (24) are respectively arranged at the upper end and the lower end of the outer oblique wing rotor (4), the roller supports (24) are provided with inclined planes, the inclined planes and the vertical plane form a certain inclined angle, and the two roller supports (24) are characterized by being in a 180-degree array by taking the axis of the valve core (9) as a central axis; the roller (23) is arranged in a groove of the roller support (24), and the linear bearing (32) is embedded in a guide hole of the wedge block (29) and is in interference fit with the guide hole of the wedge block (29); the wedge blocks (29) are sleeved on the guide rail (31) through linear bearings (32), and the guide rail (31) is arranged in rectangular windows at the upper end and the lower end of the support frame (6); a clearance compensation spring (30) is arranged between the wedge-shaped block (29) and the rectangular window, when the roller support (24) is in a neutral state, the roller (23) is in direct contact with the wedge-shaped block (29), and the clearance compensation springs (30) at two sides are in a state of neither compression nor extension;
the output rod of the bidirectional proportion electromagnet (1) is connected with a pushing rod (19) through a cylindrical pin (28), and the right end of the pushing rod (19) penetrates through the inner hole of the outer oblique wing rotor (4); thrust roller bearings (27) are respectively arranged at two sides of an inner shoulder of a hole of the outer inclined wing rotor (4) so as to prevent parts from being worn out caused by the fact that the outer inclined wing rotor (4) drives the proportional electromagnet (1) and the push rod (19) to rotate in the rotating process; the thrust roller bearing (27) is tightly pressed on the shoulder of the outer oblique wing rotor (4) through the displacement limiting block (25) and the second screw (26) so as to ensure the one-dimension of the output rod and the pushing rod (19) of the bidirectional proportional electromagnet (1);
the right end of the bidirectional proportional electromagnet (1) is sequentially connected with a proportional electromagnet base (2), a middle end cover (3), a support frame (6), an inserting end cover (7) and a valve body (11); the valve body (11) is provided with a T port, an A port, a P port, a B port and a T port in sequence, wherein the P port is an oil inlet, the pressure at the P port is the system pressure, the two T ports are communicated through a flow passage on the valve sleeve (10), the middle part of the valve core (9) is provided with two steps, and the two middle shoulders are respectively positioned above the A port and the B port; the middle and left ends of the valve core (9) are respectively provided with a high-pressure hole I (a) and a high-pressure hole II (b) which are respectively communicated with a P port and a left sensitive cavity g, so that the left sensitive cavity g is constantly communicated with high pressure, the rightmost step of the valve core (9) is respectively provided with a high-pressure hole III (c) communicated with the high-pressure P port and a low-pressure groove (f) communicated with an oil return T port, the inner surface of the rightmost end of the valve sleeve (10) is provided with a pair of straight groove sensing channels (e) which are symmetrical along a central shaft by 180 degrees, one end of each straight groove sensing channel (e) is communicated with a right sensitive cavity h, the other end of each straight groove sensing channel (e) is communicated with the high-pressure hole III (c) and the low-pressure groove (f) to form a hydraulic resistance half bridge, and the hydraulic resistance half bridge controls the pressure of oil in the right sensitive cavity h through the straight groove sensing channels (e), and in the middle position state, the hydraulic resistance half bridge controls the oil pressure in the right sensitive cavity h to be exactly equal to the pressure in the left sensitive cavity g; the closed cavity formed by the concentric ring (8), the valve core (9) and the valve sleeve (10) is a left sensitive cavity (g), and the closed cavity formed by the valve core (9), the valve sleeve (10) and the right end of the plug (12) is a right sensitive cavity (h); the left spring gasket (20) is clung to the proportional electromagnet base (2), the right spring gasket (22) is clung to the middle end cover (3), the main spring (21) is arranged between the left spring gasket (20) and the right spring gasket (22), conversion between output force and displacement of the bidirectional proportional electromagnet (1) is achieved, and when the bidirectional proportional electromagnet (1) is not electrified, gaps and zero centering are eliminated.
Further, a left compression block and a right compression block (15) are arranged at the joint of the valve core (9) and the inner inclined wing rotor (18) so as to fix the relative positions of the valve core (9) and the inner inclined wing rotor (18); one end of the compaction block (15) is embedded into the inner inclined wing rotor (18) and is connected with the inner inclined wing rotor (18) through a screw, and the screw screwing depth on the compaction block (15) is adjusted to control the size of the compaction force.
Further, a plug (12) is arranged in the inner hole on the right side of the valve body (11) so as to prevent oil from leaking from the right side; the plug (12) is fixed on the valve sleeve (10) through a fixing pin (13) so as to prevent the plug (12) from being pushed by high-pressure oil; the concentric rings (8) are arranged in the inner hole at the left side of the valve sleeve (10) so as to ensure the positioning of the valve core (9) in the inner hole of the valve sleeve (10).
The beneficial effects of the invention are as follows:
1. the two-dimensional half-bridge electrohydraulic proportional reversing valve designed by the invention adopts a non-contact magnetic suspension design for the inclined wing group of the clearance compensation type magnetic suspension displacement amplification coupling, thereby fundamentally avoiding the influence of inherent friction wear and clearance on static characteristics such as linearity, symmetry and the like of the mechanical compression torsion coupling.
2. The two-dimensional half-bridge electrohydraulic proportional reversing valve designed by the invention adopts the gap compensation type displacement amplification coupling, the displacement amplification technology can convert small displacement output by the proportional electromagnet into displacement of the valve core and amplify the displacement according to the proportion, the adverse effect on the dynamic response characteristic of the electrohydraulic proportional reversing valve caused by low frequency response and slow starting of the proportional electromagnet is solved, the gap compensation can be carried out when the displacement amplification group works, and the problem that the traditional roller displacement amplification coupling is blocked due to no gap or too small gap is solved.
3. The two-dimensional half-bridge electrohydraulic proportional reversing valve designed by the invention adopts a novel structure of the double thrust ball bearing, can ensure that the outer inclined wing rotor does not drive the proportional electromagnet ejector rod to rotate together in the rotating process, ensures the one-dimension of the proportional electromagnet, reduces the abrasion of the outer inclined wing rotor and the ejector rod, prolongs the service life of parts, eliminates the structure of the original coupling double spring centering, adopts single spring centering, and saves the installation space.
4. The two-dimensional half-bridge electrohydraulic proportional reversing valve designed by the invention has the advantages that oil-free liquid flows in the valve cavity after the pressure is lost, the valve core is not influenced by the action of hydraulic force and clamping force, the electromagnetic thrust generated after the proportional electromagnet is electrified can directly drive the valve core to move, and the working principle is the same as that of the direct-acting valve at the moment, so that the pilot and direct-acting integrated control is realized.
5. The two-dimensional half-bridge type electrohydraulic proportional reversing valve designed by the invention integrates the pilot stage and the power stage on a single valve core by adopting a two-dimensional hydraulic amplifying mechanism based on double degrees of freedom of the valve core, has the characteristics of simple structure and low processing cost, and greatly improves the power-weight ratio on the basis.
Drawings
FIG. 1 is an assembly schematic diagram of a two-dimensional half-bridge electro-hydraulic proportional reversing valve based on a gap compensation displacement amplification coupling;
FIG. 2 is a schematic diagram of the assembly of the outer diagonal flap mover 4 in a single spring pair;
FIG. 3 is a schematic view of a displacement amplifying section;
FIG. 4 is a schematic diagram of a gap-compensated magnetic levitation displacement amplifying coupling;
fig. 5 is a schematic diagram of the assembly of the outer diagonal flap mover 4 and the roller support 24;
fig. 6 is an assembly schematic diagram of the inner diagonal flap mover 18 and the valve spool 9;
fig. 7 is a schematic structural view of the intermediate end cap 3;
fig. 8 is a schematic structural view of the plug-in end cap 7;
fig. 9a to 9b are schematic views of stress states of the gap compensation type magnetic suspension displacement amplifying coupling displacement amplifying group;
fig. 10a to 10c are schematic diagrams of the working principle of the displacement amplifying group and the two-dimensional half-bridge electro-hydraulic proportional reversing valve. Fig. 10a is a schematic diagram of a neutral balance state of the displacement amplifying group and the two-dimensional half-bridge electro-hydraulic proportional reversing valve, fig. 10b is a schematic diagram of a valve core 9 rotating after the displacement amplifying group and the two-dimensional half-bridge electro-hydraulic proportional reversing valve are electrified, and fig. 10c is a schematic diagram of the displacement amplifying group and the two-dimensional half-bridge electro-hydraulic proportional reversing valve core 9 moving axially and reaching a new balance state.
The attached drawings are used for identifying and describing: 1. a bidirectional proportional electromagnet; 2. a proportional electromagnet base; 3. a middle end cover; 4. an outer oblique wing mover; 5. upper oblique wing magnetic sheet; 6. a support frame; 7. inserting an end cover; 8. a concentric ring; 9. a valve core; 10. a valve sleeve; 11. a valve body; 12. a plug; 13. a fixing pin; 14. a first screw; 15. a compaction block; 16. a lower oblique wing magnetic sheet; 17. i-shaped magnetic sheets; 18. an inner oblique wing mover; 19. a push rod; 20. a left spring washer; 21. a main spring; 22. a right spring spacer; 23. a roller; 24. a roller support; 25. a displacement limiting block; 26. a second screw; 27 thrust roller bearings; 28. a cylindrical pin; 29. wedge blocks; 30. a gap compensation spring; 31. a guide rail; 32. a linear bearing; a. a high-pressure hole I; b. a high-pressure hole II; c. high pressure hole III; e. straight groove sensing channels; f. a low pressure tank; g. a left sensitive cavity; h. right sensitive cavity.
Detailed Description
The following description of the embodiments of the present invention will be made more apparent and fully hereinafter with reference to the accompanying drawings, in which some, but not all embodiments of the invention are shown. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
In the description of the present invention, it should be noted that, as the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," "outer," and the like are used for convenience in describing the present invention and simplifying the description based on the azimuth or positional relationship shown in the drawings, it should not be construed as limiting the present invention, but rather should indicate or imply that the devices or elements referred to must have a specific azimuth, be constructed and operated in a specific azimuth. Furthermore, the terms "first," "second," "third," and the like, as used herein, are used for descriptive purposes only and are not to be construed as indicating or implying any relative importance.
In the description of the present invention, it should be noted that unless explicitly stated and limited otherwise, the terms "mounted," "connected," and "connected" should be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
Referring to the drawings, the two-dimensional half-bridge electro-hydraulic proportional reversing valve based on the gap compensation displacement amplification coupling comprises a bidirectional proportional electromagnet 1, a gap compensation magnetic suspension displacement amplification coupling and a two-dimensional half-bridge electro-hydraulic proportional reversing valve body which are sequentially arranged from left to right; the two-dimensional half-bridge electro-hydraulic proportional reversing valve body comprises a valve core 9, a valve sleeve 10 and a valve body 11, wherein the valve core 9 is embedded in the valve sleeve 10, the valve sleeve 10 is embedded in the valve body 11, and the valve core 9 is connected with the two-way proportional electromagnet 1 through a gap compensation type magnetic suspension displacement amplification coupling;
the gap compensation type magnetic suspension displacement amplification coupling comprises a magnetic suspension inclined wing assembly and a displacement amplification assembly; the magnetic suspension inclined wing assembly comprises an outer inclined wing rotor 4, an upper inclined wing magnetic sheet 5, a lower inclined wing magnetic sheet 16, an I-shaped magnetic sheet 17 and an inner inclined wing rotor 18; the inclined wing surfaces on both sides of the outer inclined wing rotor 4 and the inner inclined wing rotor 18 respectively form a certain inclination angle with the horizontal plane, and are respectively characterized by 180-degree array taking the axis of the valve core 9 as a central axis; each side inclined wing surface of the outer inclined wing rotor 4 comprises an upper inclined wing surface and a lower inclined wing surface which are arranged up and down, grooves are formed in one sides of the upper inclined wing surface and the lower inclined wing surface, which are close to each other, and an upper inclined wing magnetic sheet 5 and a lower inclined wing magnetic sheet 16 are respectively embedded in the two grooves; the two side inclined wing surfaces of the inner inclined wing rotor 18 are pincer-shaped surfaces, and I-shaped magnetic sheets 17 are embedded in the pincer-shaped surfaces, so that the inner inclined wing rotor 18 is suspended between the upper inclined wing magnetic sheet 5 and the lower inclined wing magnetic sheet 16 by magnetic force; the H-shaped magnetic sheet 17 and the upper oblique wing magnetic sheet 5 or the lower oblique wing magnetic sheet 16 form a working air gap h, the magnetic suspension oblique wing assembly can form two working air gaps h with the same height, and the inner oblique wing rotor 18 can rotate for a certain angle;
the displacement amplifying assembly comprises a supporting frame 6, rollers 23, roller supports 24, wedge blocks 29, a gap compensation spring 30, a guide rail 31 and a linear bearing 32; the two roller supports 24 are respectively arranged at the upper end and the lower end of the outer oblique wing rotor 4, the roller supports 24 are provided with inclined planes, the inclined planes and the vertical plane form a certain inclination angle, and the two roller supports 24 are characterized by being in a 180-degree array taking the axis of the valve core 9 as a central axis; the roller 23 is arranged in a groove of the roller support 24, and the linear bearing 32 is embedded in a guide hole of the wedge block 29 and is in interference fit with the guide hole of the wedge block 29; the wedge-shaped blocks 29 are sleeved on the guide rail 31 through linear bearings 32, and the guide rail 31 is arranged in rectangular windows at the upper end and the lower end of the support frame 6; a clearance compensation spring 30 is arranged between the wedge-shaped block 29 and the rectangular window, when the roller support 24 is in the neutral state, the roller 23 is in direct contact with the wedge-shaped block 29, and the clearance compensation springs 30 on two sides are in a state of neither compression nor extension;
the output rod of the bidirectional proportion electromagnet 1 is connected with a pushing rod 19 through a cylindrical pin 28, and the right end of the pushing rod 19 penetrates through the inner hole of the outer oblique wing rotor 4; because the outer oblique wing rotor 4, the inner oblique wing rotor 18 and the valve core 9 of the displacement amplification type coupling have two-dimension, namely can axially move and rotate around the axis, and the ejector rod of the bidirectional proportion electromagnet 1 is connected with the push rod 19 through the cylindrical pin 28, in order to avoid the problem that parts are seriously worn due to the fact that the outer oblique wing rotor 4 drives the proportion electromagnet 1 and the push rod 19 to rotate in the rotating process, two thrust roller bearings 27 are clamped on two sides of an inner shoulder of a hole of the outer oblique wing rotor 4, and a method of tightly pressing the thrust roller bearings 27 at two ends on the shoulder of the outer oblique wing rotor 4 by using screws 26 in combination with the displacement limiting blocks 25 is used for guaranteeing one-dimension of the ejector rod of the bidirectional proportion electromagnet 1 and the push rod 19.
The leftmost bidirectional proportion electromagnet 1 is connected with the proportion electromagnet base 2 through a screw, the proportion electromagnet base 2 is fixed on the middle end cover 3 through the screw, the support frame 6 is connected with the middle end cover 3 through the screw and is fixed on the inserting end cover 7 through the first screw 14, the valve sleeve 10 is screwed with the inserting end cover 7 through threads, and the inserting end cover 7 is connected with the valve body 11 through the screw. A plug 12 is arranged in an inner hole on the right side of the valve body 11 so as to prevent oil from leaking from the right side; the plug 12 is fixed on the valve sleeve 10 through a fixing pin 13 so as to prevent the plug 12 from being pushed by high-pressure oil liquid; the left inner hole of the valve sleeve 10 is provided with concentric rings 8 to ensure the positioning of the valve core 9 in the inner hole of the valve sleeve 10. The joint of the valve core 9 and the inner inclined wing rotor 18 is provided with a left compression block 15 and a right compression block 15 so as to fix the relative positions of the valve core 9 and the inner inclined wing rotor 18; one end of the compaction block 15 is embedded into the inner inclined wing rotor 18 and is connected with the inner inclined wing rotor 18 through screws, and the screwing depth of the screws on the compaction block 15 is adjusted to control the compaction force.
The valve body 11 is provided with a T port, an A port, a P port, a B port and a T port in sequence, wherein the P port is an oil inlet, the pressure is the system pressure, the two T ports are communicated through a flow passage on the valve sleeve 10, the middle part of the valve core 9 is provided with two steps, and two middle shoulders are respectively positioned above the A port and the B port; the middle and left ends of the valve core 9 are respectively provided with a high-pressure hole Ia and a high-pressure hole IIb which are respectively communicated with a P port and a left sensitive cavity g, so that the left sensitive cavity g is constantly communicated with high pressure, the rightmost step of the valve core 9 is respectively provided with a high-pressure hole IIIc communicated with the high-pressure P port and a low-pressure groove f communicated with an oil return T port, the inner surface of the rightmost end of the valve sleeve 10 is provided with a pair of straight groove sensing channels e which are symmetrical along a central shaft by 180 degrees, one end of each straight groove sensing channel e is communicated with a right sensitive cavity h, the other end of each straight groove sensing channel e is communicated with the high-pressure hole IIIc and the low-pressure groove f to form a hydraulic resistance half bridge, and the hydraulic resistance half bridge controls the pressure of oil in the right sensitive cavity h through the straight groove sensing channels e; the closed cavity formed by the concentric ring 8, the valve core 9 and the valve sleeve 10 is a left sensitive cavity g, and the closed cavity formed by the valve core 9, the valve sleeve 10 and the right end of the plug 12 is a right sensitive cavity h; the left spring gasket 20 is tightly attached to the proportional electromagnet base 2, the right spring gasket 22 is tightly attached to the middle end cover 3, the main spring 21 is arranged between the left spring gasket 20 and the right spring gasket 22, conversion between output force and displacement of the bidirectional proportional electromagnet 1 is achieved, and when the bidirectional proportional electromagnet 1 is not electrified, gaps and zero centering are eliminated.
The working principle of the invention is shown in figures 10 a-10 c. When the two-way proportional electromagnet 1 of the two-dimensional electro-hydraulic proportional reversing valve is not electrified, as shown in FIG. 10a, the main spring 21 is eliminatedUnder the action of the gap and zero centering, the outer oblique wing rotor 4 is in a neutral state. The upper oblique wing magnetic sheet 5, the lower oblique wing magnetic sheet 16 and the I-shaped magnetic sheet 17 of the magnetic suspension oblique wing group have the same height (the height of the air gap is h) of the upper oblique wing sheet and the lower oblique wing sheet, so that the repulsive force applied to the upper wing surface and the lower wing surface of the inner oblique wing rotor 18 is equal (equal in size and opposite in direction), and the oblique wing surfaces of the inner oblique wing rotor 18 are arranged in a 180-degree array with the central shaft as the center, so that the inner oblique wing rotor 18 can be subjected to the action of two couple moments with equal size and opposite directions, and then the inner oblique wing rotor 18 and the valve core 9 are in a balanced state; the roller 23 is in direct contact with the wedge 29 when the displacement amplifying group is in the neutral state, and the gap compensation springs 30 on both sides are in a state of neither compression nor extension. When the two-way proportional electromagnet 1 of the two-dimensional electro-hydraulic proportional reversing valve outputs F rightwards m As shown in fig. 10b, the compression amount of the main spring 21 increases, and the increased spring force and the thrust force F generated by the bidirectional proportional electromagnet 1 m And the magnetic suspension displacement amplification coupling integrally moves rightwards. At this time, the upper inclined-wing magnetic sheet 5, the lower inclined-wing magnetic sheet 16 and the I-shaped magnetic sheet 17 of the magnetic levitation inclined-wing group have their upper and lower inclined air gap heights changed correspondingly (the air gap height is h) 1 And h 2 ) Wherein the working air gap between the upper oblique wing magnetic sheet 5 and the I-shaped magnetic sheet 17 is reduced from h to h 1 The working air gap between the lower inclined wing magnetic sheet 16 and the I-shaped magnetic sheet 17 is increased from h to h 2 The magnetic repulsive force of the upper airfoil surface of the inner inclined-wing rotor 18 is increased and the magnetic repulsive force of the lower airfoil surface is reduced, and because the inclined airfoil surfaces of the inner inclined-wing rotor 18 are arranged in a 180-degree array with the central axis as the center, the inner inclined-wing rotor 18 and the valve core 9 can rotate anticlockwise (seen from right to left) under the torque action, meanwhile, for the displacement amplification group, since the wedge block 29 is directly contacted with the roller 23, the roller support 24 is connected with the outer inclined-wing rotor 4 into a whole by screws, when the outer inclined-wing rotor 4 moves rightwards, the roller 23 and the roller support 24 are driven to move rightwards together, no gap exists between the roller 23 and the wedge block 29 before the outer inclined-wing rotor 4 moves rightwards, no rotation occurs, and when the outer inclined-wing rotor 4 moves rightwards, the roller 23 pushes the wedge block 29 to compress the gap compensation spring 30 to compensate a gap, and when the outer inclined-wing rotor 4 moves rightwardsAfter the spring has compressed to a certain extent, the spring force F will be applied due to the inclined surface of the wedge-shaped block 29 t Is decomposed into a force-driving force F a As shown in fig. 9, the driving force F a The outer oblique wing rotor 4 is driven to rotate anticlockwise by delta alpha, so that a working air gap h between the upper oblique wing magnetic sheet 5 and the I-shaped magnetic sheet 17 is formed 1 Further reducing the working air gap h between the lower diagonal airfoil magnetic sheet 16 and the I-shaped magnetic sheet 17 2 Further increase, the inner oblique wing mover 18 rotates again by a certain angle, so pushing the outer oblique wing mover 4 once can obtain the effect of rotating the inner oblique wing mover 18 twice. With the rotation of the inner inclined vane mover 18 and the valve core 9, the flow areas of the straight slot sensing channel e on the inner surface of the rightmost end of the valve sleeve 10 and the high pressure hole iii c and the low pressure slot f on the rightmost step of the valve core 9 will change correspondingly, wherein the flow area of the high pressure hole iii c and the straight slot sensing channel e is reduced, the flow area of the low pressure slot f and the straight slot sensing channel e is increased, so the oil pressure in the right sensitive chamber h is reduced, while the oil pressure in the left sensitive chamber g is kept unchanged, the valve core 9 is pushed to move rightwards by the differential pressure Δx, as shown in fig. 10c, during the right movement of the valve core 9 and the inner inclined vane mover 18, the height of the inclined air gap of the coupling joint will change again due to the inclined vane structure of the outer inclined vane mover 4, the magnetic repulsive force exerted on the upper airfoil surface of the inner inclined vane mover 18 is reduced, the magnetic repulsive force exerted on the lower airfoil surface is increased, as can be seen by the force analysis of the force analysis, so that the valve core 9 rotates synchronously (i.e clockwise) until h 1 Increase to h, h 2 When the pressure is reduced to h, the stress on the two sides of the inner inclined wing rotor 18 is the same, and an equilibrium state is achieved at a new position, at this time, the oil port B is an oil supply port, the oil port A is an oil return port, and the actuating mechanism is controlled to perform corresponding actions. After the two-way proportional electromagnet 1 of the two-dimensional electro-hydraulic proportional reversing valve is powered off, the two-way proportional electromagnet 1 does not generate thrust F any more m The outer diagonal vane mover 4 is pulled back to the null position by the main spring 21, at which time the inner diagonal vane mover 18 and the valve spool 9 are returned to the null position according to the principle steps described above. When the bidirectional proportional electromagnet 1 of the two-dimensional electro-hydraulic proportional reversing valve outputs F leftwards m The situation is reversed when pulling force is applied.
The embodiments described in the present specification are merely examples of implementation forms of the inventive concept, and the scope of protection of the present invention should not be construed as being limited to the specific forms set forth in the embodiments, and the scope of protection of the present invention and equivalent technical means that can be conceived by those skilled in the art based on the inventive concept.

Claims (3)

1. The two-dimensional half-bridge electro-hydraulic proportional reversing valve based on the gap compensation displacement amplification coupling is characterized in that: the two-dimensional half-bridge electro-hydraulic proportional reversing valve comprises a two-way proportional electromagnet (1), a gap compensation type magnetic suspension displacement amplification coupling and a two-dimensional half-bridge electro-hydraulic proportional reversing valve body which are sequentially arranged from left to right; the two-dimensional half-bridge electro-hydraulic proportional reversing valve body comprises a valve core (9), a valve sleeve (10) and a valve body (11), wherein the valve core (9) is embedded in the valve sleeve (10), the valve sleeve (10) is embedded in the valve body (11), and the valve core (9) is connected with the bidirectional proportional electromagnet (1) through a gap compensation type magnetic suspension displacement amplification coupling;
the gap compensation type magnetic suspension displacement amplification coupling comprises a magnetic suspension inclined wing assembly and a displacement amplification assembly; the magnetic suspension inclined wing assembly comprises an outer inclined wing rotor (4), an upper inclined wing magnetic sheet (5), a lower inclined wing magnetic sheet (16), an I-shaped magnetic sheet (17) and an inner inclined wing rotor (18); the inclined wing surfaces on both sides of the outer inclined wing rotor (4) and the inner inclined wing rotor (18) form a certain inclination angle with the horizontal plane, and are all characterized by 180-degree array taking the axis of the valve core (9) as a central axis; each side inclined wing surface of the outer inclined wing rotor (4) comprises an upper inclined wing surface and a lower inclined wing surface which are arranged up and down, a groove is formed in one side of each upper inclined wing surface and one side of each lower inclined wing surface, which are close to each other, and an upper inclined wing magnetic sheet (5) and a lower inclined wing magnetic sheet (16) are respectively embedded in the two grooves; the two side inclined wing surfaces of the inner inclined wing rotor (18) are pincerlike surfaces, and I-shaped magnetic sheets (17) are embedded in the pincerlike surfaces, so that the inner inclined wing rotor (18) is suspended between the upper inclined wing magnetic sheet (5) and the lower inclined wing magnetic sheet (16) by magnetic force; two working air gaps h with the same height are formed between the upper surface of the I-shaped magnetic sheet (17) and the upper oblique wing magnetic sheet (5) and between the lower surface of the I-shaped magnetic sheet (17) and the lower oblique wing magnetic sheet (16), and the inner oblique wing rotor (18) can rotate;
the displacement amplifying assembly comprises a supporting frame (6), rollers (23), roller supports (24), wedge blocks (29), a clearance compensation spring (30), a guide rail (31) and a linear bearing (32); the two roller supports (24) are respectively arranged at the upper end and the lower end of the outer oblique wing rotor (4), the roller supports (24) are provided with inclined planes, the inclined planes and the vertical plane form a certain inclined angle, and the two roller supports (24) are characterized by being in a 180-degree array by taking the axis of the valve core (9) as a central axis; the roller (23) is arranged in a groove of the roller support (24), and the linear bearing (32) is embedded in a guide hole of the wedge block (29) and is in interference fit with the guide hole of the wedge block (29); the wedge blocks (29) are sleeved on the guide rail (31) through linear bearings (32), and the guide rail (31) is arranged in rectangular windows at the upper end and the lower end of the support frame (6); a clearance compensation spring (30) is arranged between the wedge-shaped block (29) and the rectangular window, when the roller support (24) is in a neutral state, the roller (23) is in direct contact with the wedge-shaped block (29), and the clearance compensation springs (30) at two sides are in a state of neither compression nor extension;
the output rod of the bidirectional proportion electromagnet (1) is connected with a pushing rod (19) through a cylindrical pin (28), and the right end of the pushing rod (19) penetrates through the inner hole of the outer oblique wing rotor (4); thrust roller bearings (27) are respectively arranged at two sides of an inner shoulder of an inner hole of the outer inclined wing rotor (4) so as to prevent parts from being worn out caused by the fact that the outer inclined wing rotor (4) drives the bidirectional proportional electromagnet (1) and the push rod (19) to rotate in the rotating process; the thrust roller bearing (27) is tightly pressed on the shoulder of the outer oblique wing rotor (4) through the displacement limiting block (25) and the second screw (26) so as to ensure the one-dimension of the output rod and the pushing rod (19) of the bidirectional proportional electromagnet (1);
the right end of the bidirectional proportional electromagnet (1) is sequentially connected with a proportional electromagnet base (2), a middle end cover (3), a support frame (6), an inserting end cover (7) and a valve body (11); the valve body (11) is provided with a T port, an A port, a P port, a B port and a T port in sequence, wherein the P port is an oil inlet, the pressure at the P port is the system pressure, the two T ports are communicated through a flow passage on the valve sleeve (10), the middle part of the valve core (9) is provided with two steps, and the two middle shoulders are respectively positioned above the A port and the B port; the middle and left ends of the valve core (9) are respectively provided with a high-pressure hole I (a) and a high-pressure hole II (b) which are respectively communicated with a P port and a left sensitive cavity (g), so that the left sensitive cavity (g) is constantly communicated with high pressure, the rightmost step of the valve core (9) is respectively provided with a high-pressure hole III (c) communicated with the high-pressure P port and a low-pressure groove (f) communicated with an oil return T port, the inner surface of the rightmost end of the valve sleeve (10) is provided with a pair of straight groove sensing channels (e) which are symmetrical along a central shaft by 180 degrees, one end of each straight groove sensing channel (e) is communicated with a right sensitive cavity (h), the other end of each straight groove sensing channel (e) is communicated with the high-pressure hole III (c) and the low-pressure groove (f) to form a hydraulic resistance half bridge, and the resistance half bridge controls the pressure of oil in the right sensitive cavity (h) through the straight groove sensing channels (e), and when the roller support (24) is in a neutral state, the hydraulic resistance half bridge controls the pressure of the oil in the right sensitive cavity (h) to be exactly equal to the pressure of the oil in the left sensitive cavity (g); the closed cavity formed by the concentric ring (8), the valve core (9) and the valve sleeve (10) is a left sensitive cavity (g), and the closed cavity formed by the valve core (9), the valve sleeve (10) and the right end of the plug (12) is a right sensitive cavity (h); the left spring gasket (20) is tightly attached to the proportional electromagnet base (2), the right spring gasket (22) is tightly attached to the middle end cover (3), the main spring (21) is arranged between the left spring gasket (20) and the right spring gasket (22), conversion between output force and displacement of the bidirectional proportional electromagnet (1) is achieved, and when the bidirectional proportional electromagnet (1) is not electrified, the functions of eliminating gaps and zero centering are achieved.
2. The two-dimensional half-bridge electro-hydraulic proportional reversing valve based on the gap compensation displacement amplification coupling as claimed in claim 1, wherein: the joint of the valve core (9) and the inner inclined wing rotor (18) is provided with a left compression block (15) and a right compression block (15) so as to fix the relative positions of the valve core (9) and the inner inclined wing rotor (18); one end of the compaction block (15) is embedded into the inner inclined wing rotor (18) and is connected with the inner inclined wing rotor (18) through a screw, and the screw screwing depth on the compaction block (15) is adjusted to control the size of the compaction force.
3. The two-dimensional half-bridge electro-hydraulic proportional reversing valve based on the gap compensation displacement amplification coupling as claimed in claim 1, wherein: a plug (12) is arranged in an inner hole on the right side of the valve body (11) so as to prevent oil from leaking from the right side; the plug (12) is fixed on the valve sleeve (10) through a fixing pin (13) so as to prevent the plug (12) from being pushed by high-pressure oil; the concentric rings (8) are arranged in the inner hole at the left side of the valve sleeve (10) so as to ensure the positioning of the valve core (9) in the inner hole of the valve sleeve (10).
CN202110433316.XA 2021-04-22 2021-04-22 Two-dimensional half-bridge electrohydraulic proportional reversing valve based on gap compensation displacement amplification coupling Active CN113107918B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202110433316.XA CN113107918B (en) 2021-04-22 2021-04-22 Two-dimensional half-bridge electrohydraulic proportional reversing valve based on gap compensation displacement amplification coupling

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202110433316.XA CN113107918B (en) 2021-04-22 2021-04-22 Two-dimensional half-bridge electrohydraulic proportional reversing valve based on gap compensation displacement amplification coupling

Publications (2)

Publication Number Publication Date
CN113107918A CN113107918A (en) 2021-07-13
CN113107918B true CN113107918B (en) 2023-05-23

Family

ID=76719297

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202110433316.XA Active CN113107918B (en) 2021-04-22 2021-04-22 Two-dimensional half-bridge electrohydraulic proportional reversing valve based on gap compensation displacement amplification coupling

Country Status (1)

Country Link
CN (1) CN113107918B (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113775586B (en) * 2021-08-18 2024-07-19 浙江工业大学 Two-dimensional full-bridge electro-hydraulic proportional reversing valve based on pincer displacement amplification coupling
CN113446415B (en) * 2021-09-01 2021-11-26 成都康拓兴业科技有限责任公司 High-efficiency low-energy-consumption electromagnetic valve for molecular sieve oxygen system in helicopter

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3308574A1 (en) * 1983-03-10 1984-09-13 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 8000 München CONTROL VALVE
WO2007102912A2 (en) * 2005-12-15 2007-09-13 Parker-Hannifin Corporation Adjustable pressure control valves
WO2009097703A1 (en) * 2008-02-04 2009-08-13 Moog Procontrol Ag Highly dynamic proportional valve
CN111075785B (en) * 2019-09-10 2024-06-11 浙江工业大学 High-flow two-dimensional half-bridge type electrohydraulic proportional reversing valve based on bidirectional magnetic suspension coupling
CN110778730A (en) * 2019-11-29 2020-02-11 佛山格尼斯磁悬浮技术有限公司 Bypass valve for magnetic suspension centrifugal blower
CN111486149B (en) * 2020-05-26 2024-07-09 青岛鸿合数字技术有限公司 Servo-assistance hydraulic cylinder

Also Published As

Publication number Publication date
CN113107918A (en) 2021-07-13

Similar Documents

Publication Publication Date Title
US9970464B1 (en) Pre-tensioning-pre-twisting full-bridge 2D electro-hydraulic proportional directional valve
CN113107918B (en) Two-dimensional half-bridge electrohydraulic proportional reversing valve based on gap compensation displacement amplification coupling
CN112984198B (en) Two-dimensional half-bridge electro-hydraulic proportional reversing valve based on push rod middle-positioned roller coupling
CN111140562B (en) Plug-in type two-dimensional magnetic suspension servo proportional valve with static pressure support
CN103711945B (en) Monofocal prestretching-pretwist type full-bridge type 2D electro-hydraulic proportion reversing valve
CN111075785B (en) High-flow two-dimensional half-bridge type electrohydraulic proportional reversing valve based on bidirectional magnetic suspension coupling
CN102913496B (en) Bi-directional full-bridge 2D electro-hydraulic proportional directional valve
CN103615572B (en) Prestretching-pretwist type simplifies full-bridge type 2D electro-hydraulic proportion reversing valve
CN203641579U (en) 2D electro-hydraulic proportion reversing valve of single-end type pretensioning-pretwisting full-bridge type
CN110617246B (en) Two-dimensional half-bridge type electrohydraulic proportional reversing valve based on Halbach array bidirectional magnetic suspension coupling
Urata et al. Development of a water hydraulic servovalve
CN112065797B (en) Two-dimensional electrohydraulic servo proportional valve based on permanent magnet type annular air gap magnetic suspension coupling
CN212899209U (en) Two-dimensional electro-hydraulic servo proportional valve based on permanent magnet type annular air gap magnetic suspension coupling
CN211778286U (en) Plug-in type two-dimensional magnetic suspension servo proportional valve with static pressure support
EP3406949B1 (en) Spool valve
CN211116881U (en) Large-flow two-dimensional half-bridge type electro-hydraulic proportional reversing valve
CN106763994B (en) Inclined wing torque motor with external coil
CN212899208U (en) Electric excitation type two-dimensional half-bridge servo proportional valve
CN113775586B (en) Two-dimensional full-bridge electro-hydraulic proportional reversing valve based on pincer displacement amplification coupling
CN108317118A (en) A kind of novel clamp button separated column plug pump swash plate variable regulating mechanism and adjusting method
CN112065796B (en) Electric excitation type two-dimensional half-bridge servo proportional valve
CN208057562U (en) A kind of novel clamp button separated column plug pump swash plate variable regulating mechanism
US9115729B2 (en) Floating action type servo-valve
CN111664139B (en) Double-freedom moment motor based on annular air gap
CN110259746B (en) Full-bridge hydraulic valve guide control mechanism

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant