CN111140562B - 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 PDFInfo
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- CN111140562B CN111140562B CN201911356358.7A CN201911356358A CN111140562B CN 111140562 B CN111140562 B CN 111140562B CN 201911356358 A CN201911356358 A CN 201911356358A CN 111140562 B CN111140562 B CN 111140562B
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- 239000000725 suspension Substances 0.000 title claims abstract description 61
- 230000003068 static effect Effects 0.000 title claims abstract description 24
- 230000033001 locomotion Effects 0.000 claims description 11
- 238000005339 levitation Methods 0.000 claims description 5
- 230000002706 hydrostatic effect Effects 0.000 claims description 3
- 230000000149 penetrating effect Effects 0.000 claims description 3
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- 230000007246 mechanism Effects 0.000 description 15
- 238000010586 diagram Methods 0.000 description 10
- 238000003825 pressing Methods 0.000 description 8
- 230000008878 coupling Effects 0.000 description 7
- 238000010168 coupling process Methods 0.000 description 7
- 238000005859 coupling reaction Methods 0.000 description 7
- 238000012545 processing Methods 0.000 description 6
- 238000000034 method Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 230000008901 benefit Effects 0.000 description 4
- 238000013461 design Methods 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 3
- 230000002035 prolonged effect Effects 0.000 description 3
- BGPVFRJUHWVFKM-UHFFFAOYSA-N N1=C2C=CC=CC2=[N+]([O-])C1(CC1)CCC21N=C1C=CC=CC1=[N+]2[O-] Chemical compound N1=C2C=CC=CC2=[N+]([O-])C1(CC1)CCC21N=C1C=CC=CC1=[N+]2[O-] BGPVFRJUHWVFKM-UHFFFAOYSA-N 0.000 description 2
- 230000003321 amplification Effects 0.000 description 2
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- 238000005516 engineering process Methods 0.000 description 2
- 230000008713 feedback mechanism Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000003199 nucleic acid amplification method Methods 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000002860 competitive effect Effects 0.000 description 1
- 239000008358 core component Substances 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010892 electric spark Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
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- 210000001503 joint Anatomy 0.000 description 1
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- 238000004519 manufacturing process Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
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- Mechanical Engineering (AREA)
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- Analytical Chemistry (AREA)
- Servomotors (AREA)
- Magnetically Actuated Valves (AREA)
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 inclined wing joint and a two-dimensional valve; the two-dimensional valve part comprises a valve core, a valve sleeve and a right end cover assembly, wherein the valve core can be rotatably and slidably arranged in an inner hole of the valve sleeve, and the left end of the valve core is provided with an extension end for connecting the magnetic suspension inclined wing joint device. The right end cover component is connected with the valve sleeve, and a P port and 2T ports on the right end cover correspond to a high-pressure oil duct P and a low-pressure oil duct T of the valve sleeve respectively; the magnetic spring comprises a left annular magnet and a right annular magnet, and is arranged between the proportional electromagnet and the magnetic suspension inclined wing joint. The left end of the two-dimensional valve is fixedly connected with the electro-mechanical converter through a magnetic suspension inclined wing joint. The outer rotor of the magnetic suspension inclined wing section is sleeved on the 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 containing cavity formed by the middle connecting end cover and the right end cover.
Description
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 electrohydraulic servo/proportional control system has wide application in the fields of aerospace, weapons, ships, large power stations, material testing machines and the like due to the core advantages of high power-weight ratio, quick dynamic response, convenient signal transmission processing after being fused with an electronic technology and the like. The electrohydraulic servo/proportional valve is used as a core component, and plays a key role in the performance of the whole system. In order to further increase the power to weight ratio and thus obtain a competitive advantage with respect to electric drive, electrohydraulic servo/proportional valves have been striving to develop in the direction of high pressure and high flow from the beginning of their birth. In order to overcome the large hydrodynamic force brought by the high-pressure large-flow working condition, the main valve core needs to be driven by hydraulic force, namely the electrohydraulic control element needs to be designed into a guide control structure. Among the innovations of a plurality of pilot control valves, the two-dimensional valve (two dimensional valve, 2D) based on the valve core double-motion degree of freedom theory and proposed by Ruan Jian and the like integrates an independent pilot stage and a power stage into a whole, integrates the two-dimensional valve on a single valve core, has the advantages of extremely high power-weight ratio, simple structure and strong pollution resistance, and is particularly applied to the occasions of military industry, aerospace and the like.
From the electro-hydraulic servo control theory angle, the two-dimensional valve is a mechanical liquid level direct feedback system, the core part of the two-dimensional valve is a feedback mechanism, the former scheme adopts a mode of processing a space spiral groove on the inner surface of a valve sleeve and forming position direct feedback with a throttle, the mode has no friction and wear problem caused by mechanical contact, the static characteristic of the valve is not influenced, the performance is excellent, but the processing difficulty of the space spiral groove is higher, an imported electric spark machine tool with more than three shafts is generally needed, the processing efficiency is low, and the valve is more suitable for high-end occasions such as military industry, aerospace and the like, and has higher popularization difficulty in the industrial field. In order to solve the problem, a feedback mechanism is moved out of a valve core valve sleeve, a special coupling is designed between an electro-mechanical converter and a flow amplifying mechanism body to serve as a feedback and motion converting link, meanwhile, thrust is amplified, a roller-sliding wedge coupling is a typical representation of the mechanical feedback amplifying mechanism, the valve is simple in structure and low in manufacturing cost, can be in butt joint with any direct-acting electro-mechanical converter, but has the main defects that friction and abrasion generated by a roller-sliding wedge friction pair of the valve have obvious influence on static precision (hysteresis and resolution) of the valve, and experiments show that the hysteresis of the valve still reaches 13.9% even under the condition of superposition of vibration. Other mechanical feedback amplification mechanisms such as ball screw type have been tried later, but the problems caused by friction are still difficult to solve due to the nature of mechanical contact. The magnetic suspension torsion pressing mechanism adopts a non-contact magnetic suspension design at the inclined plane, so that the influence of mechanical feedback amplification mechanism on the linearity, repeatability, hysteresis and other static characteristics of the valve due to clearance and friction wear is avoided, but the linear bearing in the mechanism has the influence of sliding friction. In addition, a scheme of a permanent magnet linear guide type magnetic suspension torque pressing mechanism is tried, the magnetic suspension torque pressing mechanism adopts a magnetic suspension design at an inclined plane, axial movement of the torque pressing mechanism is realized by using a permanent magnet linear guide, friction at a linear bearing is eliminated, but the torque pressing mechanism rotates due to insufficient magnetic rigidity, so that 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 static pressure support, which aims to solve the problems that a mechanical torque pressing mechanism affects the linearity, repeatability, hysteresis and other static characteristics of a two-dimensional valve, the magnetic suspension torque pressing mechanism has the influence of sliding friction, and a permanent magnet linear guide rail type magnetic suspension torque pressing 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 inclined 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 assembly, wherein the valve core 12 can rotate and can be placed in an inner hole of the valve sleeve 13 in a sliding manner, an extension end is arranged at the left end of the valve core 12 and is used for connecting a magnetic suspension inclined wing joint device, two annular grooves (k 1 and k 2) are formed in the inner hole wall of the valve sleeve 13 and are communicated with a low-pressure oil channel T of the valve sleeve 13, 2T ports, 4 full-circumference opening A ports, 6P ports and 4 full-circumference opening B ports are sequentially formed in the circumferential direction of the valve sleeve 13 between the two annular grooves (k 1 and k 2), wherein the P ports are oil inlets and are communicated with a high-pressure oil channel P of the valve sleeve 13, and the pressure is the system pressure; the left end shoulder of the valve core 12 is sleeved with a concentric ring 11, a high-pressure cavity g is formed together with the left end second shoulder of the valve core 12, the valve core 12 is provided with two high-pressure holes, namely a high-pressure hole a communicated with the high-pressure cavity g and a high-pressure hole b communicated with a P port, and the right end shoulder of the valve core 12 is also provided with a rectangular high-pressure groove c communicated with the P port and a rectangular low-pressure groove d communicated with a T port; in addition, a plug 15 is arranged in the inner hole at the right end 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 between the plug and a shoulder at the right end of the valve core 12; two rectangular sensing channels e are formed on the inner wall of the right end of the valve sleeve 13 in an axisymmetric mode, the right end of the rectangular sensing channels 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 the rectangular sensing channels and the high-pressure groove c and the low-pressure groove d of the valve core 12, and the two throttling ports are connected in series to form a hydraulic resistance half bridge, so that 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 duct P and the low-pressure oil duct 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 arranged between the proportional electromagnet 1 and a magnetic suspension inclined wing joint 21, wherein the left end face of the left magnet seat 2 is contacted with a left end cover 4 and a push rod 19 of the electromagnet 1, the right end face of the right magnet seat 6 is contacted with a middle connecting end cover 7 and an outer rotor 8, the magnetic spring 20 mainly plays roles of balancing and resetting and plays roles of eliminating gaps and zero centering (when the proportional electromagnet 1 is not electrified, a guide bridge circuit rotates and centers, and an axial opening of a main valve is in a zero centering state). The left end of the two-dimensional valve is fixedly connected with an electro-mechanical converter through a magnetic suspension inclined wing section 21.
The magnetic suspension inclined wing section 21 comprises an outer rotor 8, 4 outer rotor magnetic sheets 16, 2 inclined wing rotor magnetic sheets 17 and an inclined wing rotor 18, wherein the outer rotor 8 is sleeved on two drainage tubes 10 of the right end cover assembly to limit radial rotation of the drainage tubes, so that the outer rotor 8 can only perform 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 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 from the small hole of the drainage tube 10 through the high-pressure oil duct P from the P port of the valve sleeve 13 to fill the gap, and as the gap is not a closed space, oil overflows from two ends (gap two ends) 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 flows back to the oil tank from the T port of the right end cover 9, and in the process, the outer rotor 8 and the drainage tube 10 are always separated by a thin oil film, so that friction motion is avoided between the outer rotor 8 and the drainage tube 10, the motion precision is improved, the service life is prolonged, and hysteresis characteristics caused by friction force in the original magnetic suspension coupling are also 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 working dead zone of the valve is not caused.
Two magnetic sheet oblique grooves are respectively formed in the left side and the right side of the outer rotor 8, the outer rotor magnetic sheets 16 are adhered to the corresponding oblique grooves, and an oblique wing rotor magnetic sheet 17 is respectively arranged on the left fork-shaped wing surface and the right fork-shaped wing surface of the oblique wing rotor 18; the inclined groove of the outer rotor 8 and the fork-shaped wing surface of the inclined wing rotor 18 have the same inclined angle beta, and are characterized by 180 degrees of array taking the valve core 12 as a central axis, the inclined wing rotor 18 is arranged in the middle of the outer rotor 8, so that magnetic repulsive force is generated, and two inclined working air gaps with the same height are formed, so that the inclined wing rotor 18 is rotatably 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 0.05mm.
The beneficial effects of the invention are mainly shown in the following steps:
1. The plug-in type two-dimensional magnetic suspension servo proportional valve with the static pressure support has the advantages that the static pressure support design is adopted for the magnetic suspension inclined wing section, so that the magnetic suspension inclined wing section does not move in a friction way, the movement precision is improved, the service life is prolonged, and hysteresis characteristics caused by friction force in the original magnetic suspension coupling are 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 working dead zone of the valve is not 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 electromechanical converter, such as a switch electromagnet, a voice coil motor, a linear force motor and the like, so as to form a two-dimensional electrohydraulic control element with various purposes, such as reversing, proportion, servo and the like.
3. The cartridge type two-dimensional magnetic suspension servo proportional valve with the static pressure support adopts a two-dimensional flow amplifying mechanism with double degrees of freedom of the valve core, integrates a guide control stage and a power stage on a single valve core, simplifies the structure, reduces the processing cost and greatly improves the power-weight ratio; 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 plug-in type two-dimensional magnetic suspension servo proportional valve with the static pressure support adopts the magnetic spring mechanism to replace the spring force generated by the traditional spring compression by the magnetic repulsive force, so that the structure of the two-dimensional valve is more compact, and the installation between the electro-mechanical converter and the magnetic suspension inclined wing section is more convenient.
Drawings
FIG. 1 is an assembly schematic diagram of a cartridge two-dimensional magnetic levitation servo proportional valve with hydrostatic support;
FIG. 2 is an enlarged view of section I of FIG. 1;
Fig. 3 is a schematic diagram of the assembly of the proportional electromagnet 1 with the push rod 19;
fig. 4 is a schematic structural view of the left end cover 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 cross-sectional view of the valve housing 13, with 2 high pressure oil channels P as reference surfaces;
fig. 7b is a cross-sectional view of the valve housing 13, with 2 low pressure channels T as reference surfaces;
FIG. 8 is an exploded view of the valve sleeve assembly and right end cap assembly;
fig. 9 is a schematic diagram of the assembly structure of the magnetic spring 20, the magnetic suspension inclined 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 oblique wing section 21 and the valve core 12;
fig. 11 is a schematic diagram of the 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; fig. 12a to 12d are schematic diagrams of a movement process of the plug-in type two-dimensional magnetic suspension servo proportional valve, wherein fig. 12a is a schematic diagram of an initial equilibrium state of the plug-in type two-dimensional magnetic suspension servo proportional valve, fig. 12b is a schematic diagram of a valve core rotation after the plug-in type two-dimensional magnetic suspension servo proportional valve is electrified, fig. 12c is a schematic diagram of a valve core sliding after the plug-in type two-dimensional magnetic suspension servo proportional valve is electrified, and fig. 12d is a schematic diagram of the plug-in type two-dimensional magnetic suspension servo proportional valve reaching a new equilibrium state;
Fig. 13 is a diagram of a force analysis of a 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 a static pressure support comprises a proportional electromagnet 1, a left end cover 4, a magnetic suspension inclined wing section end cover 7, a right end cover 9, a drainage tube 10, concentric rings 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 inclined 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 assembly 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 inclined wing section and a two-dimensional valve.
The magnetic suspension inclined wing section 21 comprises an outer rotor 8, 4 outer rotor magnetic sheets 16, 2 inclined wing rotor magnetic sheets 17 and an inclined wing rotor 18, wherein the outer rotor 8 is sleeved on two drainage tubes 10 of the right end cover assembly to limit radial rotation of the drainage tubes, so that the outer rotor 8 can only perform axial linear motion; in addition, as can be seen from fig. 2, a gap of about 0.05mm 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 from the small hole of the drainage tube 10 through the high-pressure oil duct P from the P port of the valve sleeve 13 to fill the gap, and as the gap is not a closed space, oil overflows from two ends (gap two ends) 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 flows back to the oil tank from the T port of the right end cover 9, and in the process, the outer rotor 8 and the drainage tube 10 are always separated by a thin oil film, so that friction motion is avoided between the outer rotor 8 and the drainage tube 10, the motion precision is improved, the service life is prolonged, and hysteresis characteristics caused by friction force in the original magnetic suspension coupling are also 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 working dead zone of the valve is not caused.
Two magnetic sheet oblique grooves are respectively formed in the left side and the right side of the outer rotor 8, the outer rotor magnetic sheets 16 are adhered to the corresponding oblique grooves, and an oblique wing rotor magnetic sheet 17 is respectively arranged on the left fork-shaped wing surface and the right fork-shaped wing surface of the oblique wing rotor 18; the inclined groove of the outer rotor 8 and the fork-shaped wing surface of the inclined wing rotor 18 have the same inclined angle beta, and are characterized by 180 degrees of array taking the valve core 12 as a central axis, the inclined wing rotor 18 is arranged in the middle of the outer rotor 8, so that magnetic repulsive force is generated, and two inclined working air gaps with the same height are formed, 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 assembly, wherein the valve core 12 can rotate and can be slidably arranged in an inner hole of the valve sleeve 13, 5 shoulders are arranged on the valve core, and 2 of the shoulders are end shoulders; as shown in fig. 7, the inner wall of the valve sleeve 13 is provided with two annular grooves (k 1,k2) which are communicated with the low-pressure oil duct T of the valve sleeve 13; between two annular grooves (k 1,k2), the valve sleeve 13 is provided with 2T ports, 4 full-circumference opening A ports, 6P ports and 4 full-circumference opening B ports in turn 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 the system pressure; the left end shoulder of the valve core 12 is sleeved with a concentric ring 11, a high-pressure cavity g is formed together with the left end second shoulder of the valve core 12, the valve core 12 is provided with two high-pressure holes, namely a high-pressure hole a communicated with the high-pressure cavity g and a high-pressure hole b communicated with a P port, and the right end shoulder of the valve core 12 is also provided with a rectangular high-pressure groove c communicated with the P port and a rectangular low-pressure groove d communicated with a T port; in addition, a plug 15 is arranged in the inner hole at the right end 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 between the plug and a shoulder at the right end of the valve core 12; two rectangular sensing channels e are formed on the inner wall of the right end of the valve sleeve 13 in an axisymmetric mode, the right end of the rectangular sensing channels 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 the rectangular sensing channels and the high-pressure groove c and the low-pressure groove d of the valve core 12, and the two throttling ports are connected in series to form a hydraulic resistance half bridge, so that the pressure in the sensitive cavity f is controlled.
The proportional electromagnet 1 is connected with the push rod 19 through a set screw and is arranged on the 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 duct P and the low-pressure oil duct 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 arranged between the proportional electromagnet 1 and a magnetic suspension inclined wing joint 21, wherein the left end face of the magnet base 2 is contacted with a left end cover 4 and a push rod 19, the right end face of the magnet base 6 is contacted with a middle connecting end cover 7 and an outer rotor 8, and the magnetic spring 20 mainly plays roles of balancing force and converting thrust of the proportional electromagnet 1 into displacement and plays roles of eliminating gaps and zero centering (when the proportional electromagnet 1 is not electrified, a guide bridge circuit rotates and centers, and an axial opening of a main valve is in a zero centering state).
The two-dimensional valve is only connected with an electro-mechanical converter at the left end through a magnetic suspension inclined wing joint 21, wherein a valve core 13 and an inclined wing rotor 18 are axially fixed through a set screw, and an outer rotor 8 is in transitional fit connection with a push rod 19 on the proportional electromagnet 1 through a pin shaft.
The electro-mechanical converter is a commercially available proportional electromagnet mature in the market at present, and it should be noted that the driving of the magnetic suspension inclined wing section 21 is not limited to the proportional electromagnet, but may be any direct-acting electro-mechanical converter, such as a switch electromagnet, a voice coil motor, a linear force motor, etc., so as to form a two-dimensional electro-hydraulic control element with various purposes such as reversing, proportion, servo, etc. The magnetic suspension coupling 21 has the main function of converting a displacement signal output by the electro-mechanical converter into a rotation signal to 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 invention is shown in figures 12a,12b,12c,12d and 13. When the proportional electromagnet 1 is not electrified, the heights of the 4 inclined working air gaps formed by the magnetic suspension inclined wing sections 21 are equal (d 1＝d2) due to the symmetrical structure, so that the magnetic repulsive forces born by the upper and lower side wing surfaces of the inclined wing rotor 18 are equal (F 1＝F2), namely, the valve core 12 is in a balanced state. When the proportional electromagnet 1 is electrified, the outer rotor 8 of the magnetic suspension inclined wing joint 21 moves rightwards under the pushing of the proportional electromagnet 1 until the pushing force F m of the proportional electromagnet 1 is balanced with the magnetic repulsive force F s generated by the compression of the magnetic spring 20, and in the process, the outer rotor 8 stops moving, the heights of the 4 inclined working air gaps of the magnetic suspension inclined wing joint 21 change (d 1>d2), so that the magnetic repulsive force borne by the upper side wing surface and the lower side wing surface of the inclined wing rotor 18 changes (F 2>F1), the valve core 12 is not in a balanced state any more, and at the moment, the valve core 12 is subjected to the resultant force of the rightward axial driving forces F a(F1a and F 2a and the resultant force of the tangential forces F t(F1t and F 2t) in the anticlockwise direction (seen from left to right). Since the two-dimensional valve portion is under high pressure and high flow, the spool 12 is affected by the hydrodynamic force F h, which is much greater than the axial driving force F a, and thus the spool 12 cannot be directly driven to move axially. At the same time, the valve core 12 rotates counterclockwise under the influence of a magnetic moment sufficient to overcome the viscous friction (typically very small) between the valve core 12 and the valve sleeve 13, thereby rotating the valve core 12 by Δθ. Because the valve core 12 rotates anticlockwise, the communication area between the rectangular high-pressure groove (c) and the rectangular low-pressure groove (d) at the right end of the valve core 12 and the sensing channel e changes, so that the pressure of the sensing cavity f is reduced, and therefore, the valve core 12 moves rightwards by delta x axially, oil flows from the port P to the port B, and oil flows from the port A to the port T. In the right shift process, the heights of the 4 inclined working air gaps of the magnetic suspension inclined wing segments 21 are changed again (d 1<d2) due to the 180-degree array characteristic of the inclined wing rotor 18, so that the magnetic repulsive force born by the upper and lower side wing surfaces of the inclined wing rotor 18 is changed again (F 1>F2). From the above force analysis, it is known that this causes the spool 12 to rotate synchronously (i.e. clockwise) until the 4 inclined working air gaps of the magnetic levitation oblique wing section 21 become equal in height, the pressure of the sensitive chamber f is restored to the previous equilibrium value, and the spool 12 reaches a new equilibrium position. The situation is reversed when the proportional electromagnet 1 is de-energized or reverse energized.
The above-described embodiments are intended to illustrate the present invention, not to limit the present invention, and any modifications and variations made to the present invention within the spirit of the present invention and the scope of the appended claims fall within the scope of the present invention.
Claims (2)
1. Take cartridge formula two-dimensional magnetic suspension servo proportional valve of static pressure support, its characterized in that: the magnetic suspension type two-dimensional valve consists of a proportion electromagnet (1), a magnetic suspension inclined 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 assembly, wherein the valve core (12) can rotate and can be placed in an inner hole of the valve sleeve (13) in a sliding manner, the left end of the valve core (12) is provided with an extension end for connecting a magnetic suspension inclined wing joint device, the inner hole wall of the valve sleeve (13) is provided with two annular grooves (k 1, k 2) which are communicated with a low-pressure oil duct T of the valve sleeve (13), 2T ports, 4 full-circumference opening A ports, 6P ports and 4 full-circumference opening B ports are sequentially formed in the circumferential direction of the valve sleeve (13) between the two annular grooves (k 1, k 2), 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 the system pressure; the left end shoulder of the valve core (12) is sleeved with a concentric ring (11), a high-pressure cavity g is formed together with the left end second shoulder of the valve core (12), the valve core (12) is provided with two high-pressure holes, namely a high-pressure hole a communicated with the high-pressure cavity g and a high-pressure hole b communicated with a P port, and the right end shoulder of the valve core (12) is also provided with a rectangular high-pressure groove c communicated with the P port and a rectangular low-pressure groove d communicated with a T port; in addition, a plug (15) is arranged in the inner hole at the right end 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 between the plug and a shoulder at the right end part of the valve core (12); two rectangular sensing channels e are formed on the inner wall of the right end of the valve sleeve (13) in an axisymmetric manner, the right end of the rectangular sensing channels e is communicated with the sensitive cavity f, 2 throttle openings rotated by the valve core (12) are formed between the upper side and the lower side of the left end of the rectangular sensing channels and the high-pressure groove c and the low-pressure groove d of the valve core (12), and the throttle openings 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) are respectively in one-to-one correspondence with a high-pressure oil duct P and a low-pressure oil duct T of the valve sleeve (13); 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 inclined wing section (21), wherein the left end face of the left magnet seat (2) is contacted with a left end cover (4) and a push rod (19) of the electromagnet (1), and the right end face of the right magnet seat (6) is contacted with a middle connecting end cover (7) and an outer rotor (8); the left end of the two-dimensional valve is fixedly connected with an electro-mechanical converter through a magnetic suspension inclined wing section (21);
the magnetic suspension inclined wing section (21) comprises an outer rotor (8), 4 outer rotor magnetic sheets (16), 2 inclined wing rotor magnetic sheets (17) and an inclined wing rotor (18), wherein the outer rotor (8) is sleeved on two drainage tubes (10) of the right end cover assembly to limit radial rotation of the drainage tubes, so that the outer rotor (8) can only do axial linear movement; 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 containing cavity formed by the middle connecting end cover (7) and the right end cover (9); the opening 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), and the drainage tube (10) is provided with a small hole penetrating through the tube wall;
Two magnetic sheet oblique slots are respectively formed in the left side and the right side of the outer rotor (8), outer rotor magnetic sheets (16) are adhered to the corresponding oblique slots, and oblique wing rotor magnetic sheets (17) are respectively arranged on the left fork-shaped wing surface and the right fork-shaped wing surface of the oblique wing rotor (18); the inclined groove of the outer rotor (8) and the fork-shaped wing surface of the inclined wing rotor (18) have the same inclined angle b, and are characterized by being in a 180-degree array taking the valve core (12) as a central shaft, the inclined wing rotor (18) is arranged at the middle position of the outer rotor (8) so as to generate magnetic repulsive force, and an inclined working air gap with the same front and back heights is formed, so that the inclined wing rotor (18) is rotatably suspended in the middle of the outer rotor (8) by magnetic force;
The proportional electromagnet (1) is connected with the push rod (19) through a set screw and is arranged on the 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 by using screws;
the valve core (12) and the inclined wing rotor (18) are axially fixed through a set screw, and the outer rotor (8) is in transition fit connection with a push rod (19) on the proportional electromagnet (1) through a pin shaft.
2. The cartridge two-dimensional magnetic levitation servo proportional valve with hydrostatic support of claim 1, wherein: the thickness of the gap reserved between the rotor (8) and the drainage tube (10) is 0.05mm.
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112065797B (en) * | 2020-08-12 | 2024-06-11 | 浙江工业大学 | Two-dimensional electrohydraulic servo proportional valve based on permanent magnet type annular air gap magnetic suspension coupling |
| CN112065796B (en) * | 2020-08-12 | 2024-06-11 | 浙江工业大学 | Electric excitation type two-dimensional half-bridge servo proportional valve |
| 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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