CN111140562A - Plug-in type two-dimensional magnetic suspension servo proportional valve with static pressure support - Google Patents

Plug-in type two-dimensional magnetic suspension servo proportional valve with static pressure support Download PDF

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Publication number
CN111140562A
CN111140562A CN201911356358.7A CN201911356358A CN111140562A CN 111140562 A CN111140562 A CN 111140562A CN 201911356358 A CN201911356358 A CN 201911356358A CN 111140562 A CN111140562 A CN 111140562A
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CN
China
Prior art keywords
valve
pressure
magnetic suspension
end cover
right end
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CN201911356358.7A
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Chinese (zh)
Inventor
孟彬
王登
刘备
徐豪
戴铭柱
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Zhejiang University of Technology ZJUT
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Zhejiang University of Technology ZJUT
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Priority to CN201911356358.7A priority Critical patent/CN111140562A/en
Publication of CN111140562A publication Critical patent/CN111140562A/en
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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
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control means

Abstract

The plug-in type two-dimensional magnetic suspension servo proportional valve with the static pressure support consists of a proportional electromagnet, a magnetic suspension oblique wing section and a two-dimensional valve; the two-dimensional valve part comprises a valve core, a valve sleeve and a right end cover component, wherein the valve core is rotatably and slidably arranged in an inner hole of the valve sleeve, and the left end of the valve core is provided with an elongated end for connecting the magnetic suspension oblique wing section device. The right end cover component is connected with the valve sleeve, and the P port and the 2T ports on the right end cover respectively correspond to the high-pressure oil duct P and the low-pressure oil duct T of the valve sleeve; the magnetic spring comprises a left annular magnet and a right annular magnet which are arranged between the proportional electromagnet and the magnetic suspension oblique wing sections. The left end of the two-dimensional valve is fixedly connected with the electro-mechanical converter through a magnetic suspension oblique wing section. The external rotor of the magnetic suspension oblique wing section is sleeved on two drainage tubes of the right end cover assembly; a gap is reserved between the outer rotor and the drainage tube so as to form an oil film required by static pressure support, and the gap is communicated with a cavity formed by the middle connecting end cover and the right end cover.

Description

Plug-in type two-dimensional magnetic suspension servo proportional valve with static pressure support
Technical Field
The invention belongs to a flow and reversing control valve for an electro-hydraulic proportional control technology in the field of fluid transmission and control, and particularly relates to a plug-in type two-dimensional magnetic suspension servo proportional valve with a static pressure support.
Background
The electro-hydraulic servo/proportional control system has the core advantage of high power-weight ratio, and has the advantages of fast dynamic response, convenient signal transmission and processing after being fused with an electronic technology and the like, so that the electro-hydraulic servo/proportional control system is widely applied to the fields of aerospace, weapons, ships, large-scale power stations, material testing machines and the like. The electro-hydraulic servo/proportional valve is used as a core component and plays a critical influence on the performance of the whole system. In order to further increase the power-to-weight ratio and thereby gain a competitive advantage over electric drives, electro-hydraulic servo/proportional valves strive to move towards high pressures and flows since birth. In order to overcome the large hydraulic power brought by the working condition of high pressure and large flow, the main valve core needs to be driven by hydraulic pressure, namely, the electro-hydraulic control element needs to be designed into a guide control type structure. Among numerous guide control valve structure innovations, the two-dimensional valve (2D) based on the valve core double-motion freedom theory, which is proposed by Raney Key and the like, combines an independent pilot stage and a power stage into a whole, is integrated on a single valve core, has the advantages of particularly high power-weight ratio, simple structure and strong pollution resistance, and is specifically applied to the occasions of military industry, aerospace and the like.
From the perspective of electro-hydraulic servo control theory, the two-dimensional valve is a liquid level position direct feedback system, the core part of the two-dimensional valve is a feedback mechanism, the position direct feedback is formed by a mode of machining a space spiral groove on the inner surface of a valve sleeve and a throttling opening in the early scheme, the mode has no problem of friction and abrasion caused by mechanical contact, the static characteristic of the valve is not influenced, the performance is excellent, but the machining difficulty of the inner space spiral groove is high, an imported electric spark machine tool with more than three shafts is generally needed, and the machining efficiency is low, so that the two-dimensional valve is suitable for being used in high-end occasions such as military industry and aerospace, and is high in popularization difficulty in the industrial. In order to solve the problem, a feedback mechanism is moved out of a valve core and a valve sleeve, a special coupling is designed between an electromechanical converter and a flow amplifying mechanism body to serve as a feedback and motion conversion link, meanwhile, the thrust is amplified, and a roller-sliding wedge type coupling is a typical representative of the mechanical feedback amplifying mechanism, the valve is simple in structure and low in manufacturing cost, can be butted with any direct-acting electromechanical converter, but has the main defects that the influence of frictional wear and the like generated by a roller-sliding wedge friction pair on the static accuracy (hysteresis and resolution) of the valve is obvious, and experiments show that the hysteresis of the valve still reaches 13.9% even under the condition of superimposed chatter. Other mechanical feedback amplification mechanisms such as a ball screw type mechanism are tried subsequently, but the problems caused by friction are difficult to solve due to the nature of mechanical contact. Although the magnetic suspension pressure-torsion mechanism adopts a non-contact magnetic suspension design at the inclined plane, the influence of the mechanical feedback amplification mechanism on the static characteristics of the valve such as linearity, repeatability and hysteresis loop caused by clearance and friction and abrasion is avoided, but the influence of sliding friction still exists at the linear bearing in the mechanism. In addition, a scheme of a permanent magnet linear guide rail type magnetic suspension pressing and twisting mechanism is also tried, the mechanism adopts a magnetic suspension design at an inclined plane of the magnetic suspension pressing and twisting mechanism, the permanent magnet linear guide rail is used for realizing the axial movement of the pressing and twisting mechanism, the friction at a linear bearing is eliminated, but the pressing and twisting mechanism rotates due to insufficient magnetic rigidity, and therefore a working dead zone is brought to a valve.
Disclosure of Invention
The invention provides a plug-in type two-dimensional magnetic suspension servo proportional valve with a static pressure support, which aims to solve the problems that a mechanical pressure-torsion mechanism affects the static characteristics of the linearity, the repeatability, the hysteresis loop and the like of a two-dimensional valve, sliding friction exists in a magnetic suspension pressure-torsion mechanism, and a permanent magnet linear guide rail type magnetic suspension pressure-torsion mechanism causes a working dead zone of the two-dimensional valve due to insufficient magnetic rigidity.
The invention relates to a plug-in type two-dimensional magnetic suspension servo proportional valve with a static pressure support, which consists of a proportional electromagnet, a magnetic suspension oblique wing section and a two-dimensional valve. The two-dimensional valve part comprises a valve core 12, a valve sleeve 13 and a right end cover component, wherein the valve core 12 is rotatably and slidably arranged in an inner hole of the valve sleeve 13, the left end of the valve core 12 is provided with an extension end used for connecting a magnetic suspension inclined wing joint device, the inner hole wall of the valve sleeve 13 is provided with two annular grooves (k1, k2) which are communicated with a low-pressure oil duct T of the valve sleeve 13, and the valve sleeve 13 between the two annular grooves (k1, k2) is sequentially provided with 2T ports, 4 full-circumference opening ports A, 6P ports and 4 full-circumference opening ports B in the circumferential direction, wherein the P port is an oil inlet and is communicated with a high-pressure oil duct P of the valve sleeve 13, and the pressure is system pressure; a concentric ring 11 is sleeved on the shoulder at the left end part of the valve core 12 and forms a high-pressure cavity g together with the second shoulder at the left end of the valve core 12, two high-pressure holes are arranged on the valve core 12 and respectively comprise a high-pressure hole a communicated with the high-pressure cavity g and a high-pressure hole b communicated with the port P, and a rectangular high-pressure groove c communicated with the port P and a rectangular low-pressure groove d communicated with the port T are also arranged on the shoulder at the right end part of the valve core 12; in addition, a plug 15 is arranged in the right-end inner hole of the valve sleeve 13 and is axially fixed by a fixing pin 14, so that oil is prevented from leaking from the right side of the valve sleeve 13, and a sensitive cavity f is formed by the plug and the shoulder at the right end part of the valve core 12; two rectangular sensing channels e are axially symmetrically arranged on the inner wall of the right end of the valve sleeve 13, the right end of each sensing channel e is communicated with the sensitive cavity f, 2 throttling ports which are rotated by the valve core 12 are formed between the upper side and the lower side of the left end of each sensing channel e and the high-pressure groove c and the low-pressure groove d of the valve core 12 and are connected in series to form a hydraulic resistance half bridge, and therefore the pressure in the sensitive cavity f is controlled.
The right end cover assembly is in threaded connection with the valve sleeve 13, and 2P ports and 2T ports on the right end cover 9 are respectively in one-to-one correspondence with the high-pressure oil passages P and the low-pressure oil passages T of the valve sleeve 13; the magnetic spring 20 is composed of a left magnet seat 2, a right magnet seat 6, a left annular magnet 3 and a right annular magnet 5, and is installed between the proportional electromagnet 1 and the magnetic suspension oblique wing section 21, wherein the left end face of the left magnet seat 2 is in contact with the left end cover 4 and the push rod 19 of the electromagnet 1, the right end face of the right magnet seat 6 is in contact with the intermediate connection end cover 7 and the outer rotor 8, and the magnetic spring 20 mainly plays a role in force balance and reset and plays a role in eliminating gaps and zero position centering (when the proportional electromagnet 1 is not electrified, the guide control bridge circuit is in rotation centering, and the axial opening of the main valve is in a zero position centering state). The left end of the two-dimensional valve is fixedly connected with the electro-mechanical converter through a magnetic suspension oblique wing section 21.
The magnetic suspension oblique wing joint 21 part comprises an outer rotor 8, 4 outer rotor magnetic sheets 16, 2 oblique wing rotor magnetic sheets 17 and an oblique wing rotor 18, wherein the outer rotor 8 is sleeved on two drainage tubes 10 of a right end cover assembly to limit radial rotation of the outer rotor, so that the outer rotor 8 can only do axial linear motion; in addition, a gap is reserved between the outer rotor 8 and the drainage tube 10 so as to form an oil film required by static pressure support, and the gap is communicated with a cavity formed by the middle connecting end cover 7 and the right end cover 9. The open end of the drainage tube 10 passes through the right end cover 9 and the high-pressure oil duct P communicated with the valve sleeve 13, the drainage tube 10 is provided with a small hole penetrating through the tube wall, when high-pressure oil flows out of the small hole of the drainage tube 10 from the port P of the valve sleeve 13 through the high-pressure oil duct P to fill the gap, and because the gap is not a closed space, the oil can overflow from two ends (two ends of the gap) of the outer rotor 8 to fill the whole containing cavity formed by the middle connecting end cover 7 and the right end cover 9 and then flows back to the oil tank from the T port of the right end cover 9, the outer rotor 8 and the drainage tube 10 are always separated by a thin oil film in the process, so that no friction motion exists between the outer rotor 8 and the drainage tube 10, the motion precision is improved, the service life is prolonged, and the hysteresis characteristic of the; in addition, the oil film rigidity of the static pressure support is far greater than the magnetic rigidity of the permanent magnet linear guide rail type, so that the dead working area of the valve cannot be caused.
The left side and the right side of the outer rotor 8 are respectively provided with two magnetic sheet chutes, the outer rotor magnetic sheet 16 is adhered to the corresponding chute, the left fork-shaped wing surface and the right fork-shaped wing surface of the inclined wing rotor 18 are respectively provided with an inclined wing rotor magnetic sheet 17, the chute of the outer rotor 8 and the fork-shaped wing surface of the inclined wing rotor 18 have the same inclination angle β and are in a 180-degree array characteristic with the valve core 12 as a central shaft, the inclined wing rotor 18 is arranged in the middle of the outer rotor 8 to generate magnetic repulsive force so as to form front and back inclined working air gaps with the same height, and the inclined wing rotor 18 can be rotationally suspended in the middle of the outer rotor 8 purely by magnetic force.
Preferably, the thickness of the gap reserved between the mover 8 and the draft tube 10 is 0.05 mm.
The invention has the following beneficial effects:
1. according to the cartridge type two-dimensional magnetic suspension servo proportional valve with the static pressure support, the magnetic suspension oblique wing sections adopt the design of the static pressure support, so that the magnetic suspension oblique wing sections do not move in a friction mode, the movement precision is improved, the service life is prolonged, and the hysteresis loop characteristic caused by friction force in the original magnetic suspension coupling is eliminated. In addition, the oil film rigidity of the static pressure support is far greater than the magnetic rigidity of the permanent magnet linear guide rail type, so that the dead working area of the valve cannot be caused.
2. The invention designs a plug-in type two-dimensional magnetic suspension servo proportional valve with a static pressure support, wherein a magnetic suspension coupling can be connected with any direct-acting electro-mechanical converter, such as a switch electromagnet, a voice coil motor, a linear force motor and the like, so that two-dimensional electro-hydraulic control elements with different purposes such as reversing, proportion, servo and the like are formed.
3. According to the cartridge type two-dimensional magnetic suspension servo proportional valve with the static pressure support, the two-dimensional flow amplifying mechanism with two degrees of freedom of the valve core is adopted, the pilot control stage and the power stage are integrated on the single valve core, the structure is simplified, the processing cost is reduced, and the power-weight ratio is greatly improved; in addition, the two-dimensional valve is made into a plug-in type, so that the sealing performance of the two-dimensional valve is greatly improved, and the system integration and the processing modification are easy.
4. The cartridge type two-dimensional magnetic suspension servo proportional valve with the static pressure support adopts a magnetic spring mechanism, and the spring force generated by the compression of the traditional spring is replaced by the magnetic repulsion force, so that the structure of the two-dimensional valve becomes more compact, and the installation between the electro-mechanical converter and the magnetic suspension oblique wing section becomes more convenient.
Drawings
FIG. 1 is an assembly schematic diagram of a plug-in type two-dimensional magnetic suspension servo proportional valve with a static pressure support;
FIG. 2 is an enlarged view of section I of FIG. 1;
FIG. 3 is a schematic view of the assembly of the proportional electromagnet 1 and the push rod 19;
FIG. 4 is a schematic structural view of the left end cap 4;
FIG. 5 is a schematic view of the structure of the intermediate connection end cap 7;
fig. 6 is a schematic structural view of the right end cap 9;
fig. 7a is a sectional view of the valve housing 13, which is a sectional view with 2 high-pressure oil passages P as a reference surface;
fig. 7b is a sectional view of the valve housing 13, which is a sectional view with 2 low-pressure oil passages T as reference surfaces;
fig. 8 is an exploded view of the assembled structure of the valve sleeve assembly and the right end cap assembly;
FIG. 9 is a schematic view of an assembly structure of the magnetic spring 20, the magnetic suspension oblique wing section 21 and the valve core 12;
FIG. 10 is an exploded view of the assembled structure of the magnetic spring 20, the magnetic levitation diagonal rib section 21 and the valve core 12;
FIG. 11 is a schematic view of an assembly structure of the push rod 19, the magnetic spring 20 assembly, the outer rotor 8, the left end cover 4 and the middle connecting end cover 7; 12 a-12 d are schematic diagrams of the movement process of the cartridge type two-dimensional magnetic suspension servo proportional valve, wherein fig. 12a is a schematic diagram of an initial balanced state of the cartridge type two-dimensional magnetic suspension servo proportional valve, fig. 12b is a schematic diagram of a valve core rotation after the cartridge type two-dimensional magnetic suspension servo proportional valve is electrified, fig. 12c is a schematic diagram of a valve core sliding after the cartridge type two-dimensional magnetic suspension servo proportional valve is electrified, and fig. 12d is a schematic diagram of the cartridge type two-dimensional magnetic suspension servo proportional valve reaching a new balanced state;
FIG. 13 is a force analysis diagram of the magnetic levitation oblique wing section.
Detailed Description
The invention is further described below with reference to the accompanying drawings.
A plug-in type two-dimensional magnetic suspension servo proportional valve with static pressure support comprises a proportional electromagnet 1, a left end cover 4, a magnetic suspension oblique wing section end cover 7, a right end cover 9, a drainage tube 10, a concentric ring 11, a valve core 12, a valve sleeve 13, a fixing pin 14, a plug 15, a push rod 19, a magnetic spring 20 and a magnetic suspension oblique wing section 21; the magnetic spring 20 comprises a left magnet seat 2, a right magnet seat 6, a left annular magnet 3 and a right annular magnet 5; the valve sleeve assembly comprises a valve sleeve 13, a fixing pin 14 and a plug 15; the right end cover component mainly comprises a right end cover 9 and two drainage tubes 10; the plug-in type two-dimensional magnetic suspension servo proportional valve with the static pressure support mainly comprises a proportional electromagnet, a magnetic suspension oblique wing section and a two-dimensional valve.
The magnetic suspension oblique wing joint 21 part comprises an outer rotor 8, 4 outer rotor magnetic sheets 16, 2 oblique wing rotor magnetic sheets 17 and an oblique wing rotor 18, wherein the outer rotor 8 is sleeved on two drainage tubes 10 of a right end cover assembly to limit radial rotation of the outer rotor, so that the outer rotor 8 can only do axial linear motion; in addition, as can be seen from fig. 2, a gap of about 0.05mm is reserved between the external rotor 8 and the drainage tube 10 so as to form an oil film required by hydrostatic support, and the gap is communicated with a cavity formed by the middle connecting end cover 7 and the right end cover 9. The open end of the drainage tube 10 passes through the right end cover 9 and the high-pressure oil duct P communicated with the valve sleeve 13, the drainage tube 10 is provided with a small hole penetrating through the tube wall, when high-pressure oil flows out of the small hole of the drainage tube 10 from the port P of the valve sleeve 13 through the high-pressure oil duct P to fill the gap, and because the gap is not a closed space, the oil can overflow from two ends (two ends of the gap) of the outer rotor 8 to fill the whole containing cavity formed by the middle connecting end cover 7 and the right end cover 9 and then flows back to the oil tank from the T port of the right end cover 9, the outer rotor 8 and the drainage tube 10 are always separated by a thin oil film in the process, so that no friction motion exists between the outer rotor 8 and the drainage tube 10, the motion precision is improved, the service life is prolonged, and the hysteresis characteristic of a coupling; in addition, the oil film rigidity of the static pressure support is far greater than the magnetic rigidity of the permanent magnet linear guide rail type, so that the dead working area of the valve cannot be caused.
The left side and the right side of the outer rotor 8 are respectively provided with two magnetic sheet chutes, the outer rotor magnetic sheet 16 is adhered to the corresponding chute, the left fork-shaped wing surface and the right fork-shaped wing surface of the inclined wing rotor 18 are respectively provided with an inclined wing rotor magnetic sheet 17, the chute of the outer rotor 8 and the fork-shaped wing surface of the inclined wing rotor 18 have the same inclination angle β and are in a 180-degree array characteristic with the valve core 12 as a central shaft, the inclined wing rotor 18 is arranged in the middle of the outer rotor 8 to generate magnetic repulsive force so as to form front and rear inclined working air gaps with the same height, so that the inclined wing rotor 18 is suspended in the middle of the outer rotor 8 purely by magnetic force without any mechanical structure and can rotate for a certain angle.
The two-dimensional valve part comprises a valve core 12, a valve sleeve 13 and a right end cover component, wherein the valve core 12 is rotatably and slidably arranged in an inner hole of the valve sleeve 13, and the valve core is provided with 5 shoulders, wherein 2 shoulders are end shoulders; as shown in fig. 7, the inner bore wall of the valve housing 13 has two annular grooves (k)1，k2) Which are both communicated with the low-pressure oil passage T of the valve housing 13; in two annular grooves (k)1，k2) In between, the valve sleeve 13 is sequentially provided with 2T ports, 4 all-around opening ports a, 6P ports and 4 all-around opening ports B in the circumferential direction, wherein the P port is an oil inlet and is communicated with a high-pressure oil passage P of the valve sleeve 13, and the pressure is the system pressure; a concentric ring 11 is sleeved on the shoulder at the left end part of the valve core 12 and forms a high-pressure cavity g together with the second shoulder at the left end of the valve core 12, two high-pressure holes are arranged on the valve core 12 and respectively comprise a high-pressure hole a communicated with the high-pressure cavity g and a high-pressure hole b communicated with the port P, and a rectangular high-pressure groove c communicated with the port P and a rectangular low-pressure groove d communicated with the port T are also arranged on the shoulder at the right end part of the valve core 12; in addition, a plug 15 is arranged in the right-end inner hole of the valve sleeve 13 and is axially fixed by a fixing pin 14, so that oil is prevented from leaking from the right side of the valve sleeve 13, and a sensitive cavity f is formed by the plug and the shoulder at the right end part of the valve core 12; two rectangular sensing channels e are axially symmetrically arranged on the inner wall of the right end of the valve sleeve 13, the right end of each sensing channel e is communicated with the sensitive cavity f, 2 throttling ports which are rotated by the valve core 12 are formed between the upper side and the lower side of the left end of each sensing channel e and the high-pressure groove c and the low-pressure groove d of the valve core 12 and are connected in series to form a hydraulic resistance half bridge, and therefore the pressure in the sensitive cavity f is controlled.
The proportional electromagnet 1 is connected with a push rod 19 through a set screw and is installed on a left end cover 4, and the left end cover 4, the middle connecting end cover 7 and the right end cover 9 are all fixed through screws. The right end cover assembly is in threaded connection with the valve sleeve 13, and 2P ports and 2T ports on the right end cover 9 are respectively in one-to-one correspondence with the high-pressure oil passages P and the low-pressure oil passages T of the valve sleeve 13; the magnetic spring 20 is composed of magnet bases 2 and 6 and annular magnets 3 and 5 and is installed between the proportional electromagnet 1 and the magnetic suspension oblique wing section 21, wherein the left end face of the magnet base 2 is in contact with the left end cover 4 and the push rod 19, the right end face of the magnet base 6 is in contact with the middle connecting end cover 7 and the outer rotor 8, and the magnetic spring 20 mainly plays a role in force balance and conversion of thrust of the proportional electromagnet 1 into displacement and plays a role in clearance elimination and zero position centering (when the proportional electromagnet 1 is not electrified, the pilot control bridge circuit is in rotation centering, and an axial opening of the main valve is in a zero position centering state).
Only the left end of the two-dimensional valve is connected with an electric-mechanical converter through a magnetic suspension oblique wing joint 21, wherein a valve core 13 and an oblique wing rotor 18 are axially fixed through a set screw, and an outer rotor 8 is in transition fit connection with a push rod 19 on a proportional electromagnet 1 through a pin shaft.
The electro-mechanical converter is a commercial proportional electromagnet which is mature in the market at present, and it should be noted that the driving magnetic suspension oblique wing section 21 is not limited to a proportional electromagnet, but can be any direct-acting electro-mechanical converter, such as a switch electromagnet, a voice coil motor, a linear force motor and the like, so that two-dimensional electro-hydraulic control elements with different purposes, such as commutation, proportion, servo and the like, can be formed. The magnetic suspension coupling 21 mainly functions to convert a displacement signal output by the electro-mechanical converter into a rotation signal and drive the two-dimensional valve core 12 to rotate, so that the rotation angle is within +/-2 degrees, and the translational displacement is within +/-2.5 mm.
The working principle of the implementation of the invention is shown in fig. 12a, 12b, 12c, 12d and fig. 13. When the proportional electromagnet 1 is not electrified, the heights of the 4 inclined working air gaps formed by the magnetic suspension oblique wing sections 21 are equal due to the symmetrical structure (d)1＝d2) So that the magnetic repulsion forces borne by the upper and lower wing surfaces of the oblique wing rotor 18 are equal (F)1＝F2) I.e. when the spool 12 is in equilibrium. When the proportional electromagnet 1 is electrified, the outer rotor 8 of the magnetic suspension oblique wing joint 21 moves rightwards under the pushing of the proportional electromagnet 1 until the thrust F of the proportional electromagnet 1mMagnetic repulsive force F generated by compression with the magnetic spring 20sWhen the phases are balanced, the outer rotor 8 stops moving, and the heights of the 4 inclined working air gaps of the magnetic suspension inclined wing sections 21 are changed in the process (d)1>d2) Resulting in the change of the magnetic repulsion force on the upper and lower wing surfaces of the oblique wing rotor 18 (F)2>F1) The spool 12 is no longer in equilibrium, and the spool 12 is driven axially to the rightPower Fa(F1aAnd F2aResultant force of) and from tangential force Ft(F1tAnd F2tResultant force) in a counterclockwise direction (viewed from left to right). Because the two-dimensional valve part is under high pressure and large flow, the valve core 12 is subjected to hydrodynamic force FhIs much greater than the axial driving force FaTherefore, the valve body 12 cannot be directly driven to move axially. At the same time, the spool 12 rotates counterclockwise under the influence of a magnetic torque sufficient to overcome the viscous friction (typically minimal) between the spool 12 and the sleeve 13, thereby causing the spool 12 to rotate Δ θ. Because the valve core 12 rotates anticlockwise, the communication area between the rectangular high-pressure and low-pressure grooves (c and d) at the right end of the valve core 12 and the sensing channel e changes, so that the pressure of the sensitive cavity f is reduced, the valve core 12 moves towards the right in the axial direction by delta x, oil flows from the port P to the port B, and the port A flows to the port T. During the right movement, the height of the 4 inclined working air gaps of the magnetic suspension inclined wing joint 21 changes again due to the 180-degree array characteristic of the inclined wing rotor 18 (d)1<d2) Resulting in the magnetic repulsion force exerted on the upper and lower wing surfaces of the oblique wing rotor 18 being changed again (F)1>F2). As can be seen from the foregoing force analysis, this will cause the valve core 12 to rotate back synchronously (i.e. rotate clockwise) until the 4 inclined working air gaps of the magnetic levitation diagonal wing section 21 change to the positions with equal height, the pressure in the sensing chamber f returns to the previous equilibrium value, and the valve core 12 reaches a new equilibrium position. When the proportional electromagnet 1 is de-energized or reversely energized, the situation is the opposite.
The foregoing detailed description is intended to illustrate and not limit the invention, which is intended to be within the spirit and scope of the appended claims, and any changes and modifications that fall within the true spirit and scope of the invention are intended to be covered by the following claims.

Claims (2)

1. Take cartridge formula two-dimensional magnetic suspension servo proportional valve that static pressure supported, its characterized in that: the device consists of a proportional electromagnet, a magnetic suspension oblique wing section and a two-dimensional valve; the two-dimensional valve part comprises a valve core (12), a valve sleeve (13) and a right end cover component, wherein the valve core (12) is rotatably and slidably arranged in an inner hole of the valve sleeve (13), the left end of the valve core (12) is provided with an extension end used for connecting a magnetic suspension oblique wing joint device, the inner hole wall of the valve sleeve (13) is provided with two annular grooves (k1, k2) which are communicated with a low-pressure oil duct T of the valve sleeve (13), the valve sleeve (13) between the two annular grooves (k1, k2) is sequentially provided with 2T ports, 4 full-circumference opening ports A, 6P ports and 4 full-circumference opening ports B in the circumferential direction, wherein the P ports are oil inlets and are communicated with a high-pressure oil duct P of the valve sleeve (13), and the pressure is system pressure; a concentric ring (11) is sleeved on a shoulder at the left end part of the valve core (12) and forms a high-pressure cavity g together with a second shoulder at the left end of the valve core (12), two high-pressure holes are formed in the valve core (12) and respectively comprise a high-pressure hole a communicated with the high-pressure cavity g and a high-pressure hole b communicated with the port P, and a rectangular high-pressure groove c communicated with the port P and a rectangular low-pressure groove d communicated with the port T are further formed in a shoulder at the right end part of the valve core (12); in addition, a plug (15) is arranged in the right-end inner hole of the valve sleeve (13) and is axially fixed by a fixing pin (14), so that oil is prevented from leaking from the right side of the valve sleeve (13), and a sensitive cavity f is formed by the right-end inner hole of the valve sleeve and a shoulder at the right end of the valve core (12); two rectangular sensing channels e are axially symmetrically arranged on the inner wall of the right end of the valve sleeve (13), the right end of each sensing channel e is communicated with the sensitive cavity f, 2 throttling ports rotated by the valve core (12) are formed between the upper side and the lower side of the left end of each sensing channel e and the high-pressure groove c and the low-pressure groove d of the valve core (12), and the throttling ports are connected in series to form a hydraulic resistance half bridge so as to control the pressure in the sensitive cavity f;
the right end cover assembly is in threaded connection with the valve sleeve (13), and 2P ports and 2T ports on the right end cover (9) correspond to the high-pressure oil passages P and the low-pressure oil passages T of the valve sleeve (13) one by one respectively; the magnetic spring (20) consists of a left magnet seat (2), a right magnet seat (6), a left annular magnet (3) and a right annular magnet (5), and is arranged between the proportional electromagnet (1) and the magnetic suspension oblique wing section (21), wherein the left end face of the left magnet seat (2) is in contact with the left end cover (4) and the push rod (19) of the electromagnet (1), and the right end face of the right magnet seat (6) is in contact with the middle connecting end cover (7) and the outer rotor (8); the left end of the two-dimensional valve is fixedly connected with the electro-mechanical converter through a magnetic suspension oblique wing section (21);
the magnetic suspension oblique wing joint (21) part comprises an outer rotor (8), 4 outer rotor magnetic sheets (16), 2 oblique wing rotor magnetic sheets (17) and an oblique wing rotor (18), wherein the outer rotor (8) is sleeved on two drainage tubes (10) of a right end cover assembly to limit radial rotation of the outer rotor, so that the outer rotor (8) can only do axial linear motion; in addition, a gap is reserved between the outer rotor (8) and the drainage tube (10) so as to form an oil film required by static pressure support, and the gap is communicated with a cavity formed by the middle connecting end cover (7) and the right end cover (9); the open end of the drainage tube (10) passes through the right end cover (9) and the high-pressure oil passage P communicated with the valve sleeve (13), and the drainage tube (10) is provided with a small hole penetrating through the tube wall;
the left side and the right side of the outer rotor (8) are respectively provided with two magnetic sheet chutes, outer rotor magnetic sheets (16) are adhered to the corresponding chutes, two inclined wing rotor magnetic sheets (17) are respectively installed on the left fork-shaped wing surface and the right fork-shaped wing surface of the inclined wing rotor (18), the chutes of the outer rotor (8) and the fork-shaped wing surfaces of the inclined wing rotors (18) have the same inclination angle β and are in a 180-degree array characteristic with the valve core (12) as a central shaft, and the inclined wing rotors (18) are arranged in the middle of the outer rotor (8) to generate magnetic repulsive force so as to form front and rear inclined working air gaps with the same height, so that the inclined wing rotors (18) can be rotationally suspended in the middle of the outer rotor (8) by magnetic force.
2. The cartridge type two-dimensional magnetic suspension servo proportional valve with static pressure support of claim 1, wherein: the thickness of the reserved gap between the rotor (8) and the drainage tube (10) is 0.05 mm.
CN201911356358.7A 2019-12-25 2019-12-25 Plug-in type two-dimensional magnetic suspension servo proportional valve with static pressure support Pending CN111140562A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112984198A (en) * 2021-03-15 2021-06-18 浙江工业大学 Two-dimensional half-bridge electro-hydraulic proportional reversing valve based on push rod middle-positioned roller coupling
CN113339347A (en) * 2021-06-24 2021-09-03 河南航天液压气动技术有限公司 High-pressure high-response plug-in type electro-hydraulic proportional reversing valve

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112984198A (en) * 2021-03-15 2021-06-18 浙江工业大学 Two-dimensional half-bridge electro-hydraulic proportional reversing valve based on push rod middle-positioned roller coupling
CN112984198B (en) * 2021-03-15 2022-03-18 浙江工业大学 Two-dimensional half-bridge electro-hydraulic proportional reversing valve based on push rod middle-positioned roller coupling
CN113339347A (en) * 2021-06-24 2021-09-03 河南航天液压气动技术有限公司 High-pressure high-response plug-in type electro-hydraulic proportional reversing valve

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