CN112065796A - Electric excitation type two-dimensional half-bridge servo proportional valve - Google Patents
Electric excitation type two-dimensional half-bridge servo proportional valve Download PDFInfo
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- 230000005284 excitation Effects 0.000 title claims description 37
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- 239000000725 suspension Substances 0.000 claims abstract description 20
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- 238000006073 displacement reaction Methods 0.000 description 8
- 230000003068 static effect Effects 0.000 description 7
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- 230000003321 amplification Effects 0.000 description 5
- 238000005339 levitation Methods 0.000 description 5
- 238000003199 nucleic acid amplification method Methods 0.000 description 5
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- 238000006243 chemical reaction Methods 0.000 description 2
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- 230000007547 defect Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
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- 230000004044 response Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0603—Multiple-way valves
- F16K31/061—Sliding valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
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Abstract
An electrically excited two-dimensional half-bridge servo proportional valve comprises a direct-acting linear electro-mechanical converter, an electrically excited annular air gap magnetic suspension coupling and a two-dimensional (2D) half-bridge reversing valve body which are coaxially connected in sequence. The threaded connecting rod of the electrically excited annular air gap magnetic suspension coupling body is connected with a spring resetting mechanism; two sides of the outer rotor are respectively connected with an inclined pole shoe which is characterized in that the inclined pole shoes are arrayed at an angle of 180 degrees and are vertical to the central shaft; the inner rotor is rotatably arranged between the inclined pole shoes at the two sides of the outer rotor; the inclined plane grooves on two sides of the inner rotor are arranged in an array manner of being vertical to the central shaft by 180 degrees, and the inner rotor magnetic sheets are arranged in the inclined plane grooves; the inclined plane of the inclined plane pole shoe on the same side is parallel to the inclined plane groove, and an arc-shaped air gap between the inclined plane pole shoe and the inner rotor magnetic sheet forms a working air gap for driving the valve element to rotate. The invention can reduce the working air gap and generate larger torque by using smaller magnetic sheets.
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 an electrically-excited two-dimensional half-bridge servo proportional valve.
Background
Since the advent of the electro-hydraulic servo control technology in the fortieth years of the last century, the electro-hydraulic servo control technology has occupied a high-end position in the electro-mechanical transmission and control technology due to the remarkable characteristics of high power-to-weight ratio, large output force (torque), excellent static and dynamic characteristics and the like, and is mainly applied to various strategic industrial occasions such as aerospace, military weapons, ships, large-scale power stations, steel and the like, thereby achieving great success. However, the electro-hydraulic servo valve is extremely sensitive to oil pollution, and harsh in application and maintenance conditions, and in addition, the requirement of seeking a zero-position characteristic to meet the requirement of closed-loop control is very strict in the requirements on the machining and assembling precision of key parts, so that the electro-hydraulic servo valve is difficult to be accepted by the industry, people generally expect a control technology which has reliable performance, high quality and low price, and can meet the actual requirements of an industrial control system on the control precision and the response characteristic, and the electro-hydraulic proportional control technology is developed under the background. In 1967, swiss bringer (Beringer) used a proportional electro-mechanical converter (proportional solenoid) for the first time in an industrial hydraulic valve, and the produced KL-type proportional directional valve was considered to be the earliest proportional valve in the world. In the seventh and eighties of the twentieth century, due to the application of various feedback and electric correction means such as pressure, flow, displacement, dynamic pressure and the like, the static and dynamic characteristics of the proportional valve are greatly improved, and in addition, the proportional valve is deeply integrated with the latest insertion technology, and the electro-hydraulic proportional control technology enters a golden age. By the development of the prior art, almost all traditional flow, pressure and reversing valves can find corresponding electro-hydraulic proportional valve products, and the electro-hydraulic proportional valve products are more and more widely applied to industrial production.
The proportional reversing valve requires continuous proportional positioning control of displacement (position) of a valve core, and the simplest mode is to linearly convert thrust output by a proportional electromagnet into displacement of the valve core through a spring, which is also the basic working principle of a single-stage or direct-acting proportional reversing valve or a flow valve. However, when oil flows through the valve port, a hydrodynamic force (also called bernoulli force) acts on the valve core due to the bernoulli effect, and the magnitude of the hydrodynamic force is proportional to the product of the opening area of the valve port and the pressure drop, so that the proportional characteristic of the direct-acting proportional valve is obviously deteriorated along with the increase of the pressure difference of the valve port, and even the abnormal phenomenon that the flow passing through the proportional valve is reduced on the contrary along with the increase of the pressure difference of the valve port occurs. Therefore, the principle of controlling the position of the valve core according to the balance of the thrust force and the spring force of the electromagnet is only suitable for the proportional valve with small flow, and the maximum working flow in practical application is generally below 15L/min (the maximum working pressure is 21 MPa). In addition, in order to realize the balance of axial static pressure, the direct-acting proportional reversing valve or the flow valve adopts a slide valve structure, and is easily affected by friction force and oil pollution to generate a 'clamping stagnation' phenomenon. If a direct-acting proportional reversing valve or a flow valve is required to obtain better proportional characteristics, the matching between the valve core and the valve core hole must achieve higher precision, particularly cylindricity which is sensitive to friction force. For example, the precision of the valve core of the phi 6 drift diameter proportional valve of a certain foreign company is within 1 micron, the high cylindricity is similar to the precision requirement of the valve core of the servo valve, and the high cylindricity is difficult to be realized by domestic common hydraulic part manufacturers, so that the high cylindricity is one of the main reasons for the non-ideal performance of the domestic direct-acting proportional reversing valve. The position of the valve core is measured and closed-loop controlled by a linear displacement transducer (LVDT), an electric feedback type direct-acting proportional reversing valve is formed, the positioning rigidity and the control precision of the valve core can be improved to a great extent, and finally the electric feedback type direct-acting proportional valve can be applied to the closed-loop control of a hydraulic system (the valve is called as a proportional servo valve) like a servo valve.
The most fundamental method is to adopt a pilot control technology. In 1936, in order to solve the problem that the direct-acting overflow valve cannot realize pressure control of a high-pressure and high-flow system due to the influence of hydraulic force, the Harry Vickers invented a pilot overflow valve. The idea of guiding control is widely applied to the design of other hydraulic valves, so that the high-pressure and large-flow control of a hydraulic system becomes practical. Later electro-hydraulic servo control elements also adopt the design idea of pilot control, wherein electro-hydraulic proportional valves are also included.
Among numerous guide and control level structure innovations, the flow amplification mechanism designed based on Two-Dimensional (2D or Two-Dimensional) degrees of freedom of motion of the valve core combines the originally separated guide and control level and power level into one and is integrated on a single valve core, so that the structure is simple, the dynamic response is fast, and more importantly, the pollution resistance of the valve is greatly improved. Ruan Jian and so on propose one directly move-guide control integrated 2D electric liquid proportion switching-over valve, combine 2D valve and proportion electro-magnet through pressing and twisting the amplification technique, make it have directly move and guide control electric liquid proportion switching-over valve advantage separately concurrently, plus the anti-pollution ability is strong, does not have the special high requirement to the machining precision, has fine large-scale production and applied prospect. The main problem of the valve is that a pressure-torsion coupling playing a role in pressure-torsion amplification is a roller inclined-plane mechanical mechanism, and nonlinear links such as friction force and assembly clearance exist, so that the valve has great influence on static characteristics such as linearity, repeatability and hysteresis of the electro-hydraulic proportional valve.
In order to solve the influence of a mechanical type pressure-torsion coupler of the traditional 2D electro-hydraulic proportional reversing valve on static characteristics such as linearity, repeatability, hysteresis loop and the like, Benin and the like propose a magnetic suspension coupling type electro-hydraulic servo proportional valve, and the purpose of pressure-torsion amplification is achieved by combining a magnetic suspension coupling and a proportional electromagnet. The input end and the output end of the magnetic suspension coupling are not in contact, and the torque is transmitted through the magnetic repulsion force. Therefore, the influence of inherent clearance and frictional wear on static characteristics such as linearity, repeatability and hysteresis loop of the valve is avoided. As the valve core stroke of the magnetic suspension coupling type two-dimensional servo proportional valve is +/-2 mm, the magnetic suspension coupling has the magnetic repulsive force working air gap which cannot be reduced to be very small (objective physical phenomenon: the magnetic force is exponentially increased along with the reduction of the working air gap). And a large torque is required to drive the valve core to rotate, so that a large-sized permanent magnet must be designed for torque transmission work, which limits further increase of the power-to-weight ratio. In addition, the large repulsive magnetic force makes the assembly process of the whole magnetic levitation coupling difficult. The valve body of the magnetic suspension coupling type two-dimensional servo proportional valve is a plate-type valve body, and has the defects of low flow capacity, low modularization degree, low automation degree and the like.
Disclosure of Invention
The invention aims to solve the problems of the existing magnetic suspension coupling type electro-hydraulic servo proportional valve: 1. the magnetic suspension coupling cannot achieve a very small working air gap; 2. the valve body is a plate-type valve body, so that the defects of low circulation capacity, low modularization degree, low automation degree and the like are caused.
The invention relates to an electrically-excited two-dimensional half-bridge servo proportional valve which comprises a two-dimensional (2D) half-bridge reversing valve body, an electrically-excited annular air gap magnetic suspension coupling and a direct-acting linear electro-mechanical converter 1 which are coaxially connected in sequence.
The output end of the linear electric-mechanical converter 1 is connected with a threaded connecting rod 15 of the linear electric-mechanical converter 1, the threaded connecting rod 15 is connected with a push plate 3, and the push plate 3 is connected with an outer rotor 6;
the electric excitation type annular air gap magnetic suspension coupling body comprises a left end cover 2 and a right end cover base 5 which are connected with each other; the left spring seat 16 and the right spring seat 18 are sleeved on the threaded connecting rod 15, a spring 17 is arranged between the left spring seat 16 and the right spring seat 18, and the axial positions of the left spring seat 16 and the right spring seat 18 are respectively limited by the left end cover 2 and the right end cover base 5; in order to enable the electric excitation type outer rotor 6 to only do longitudinal motion, the linear bearing 4 is sleeved on the cylinder of the push plate 3 and is arranged on the right end cover base 5.
The outer rotor 6 is approximately U-shaped, two sides of the first connecting rod are respectively connected with an inclined pole shoe, the first connecting rod is vertical to the central shaft, and an outer rotor coil 19 arranged on the first connecting rod is positioned on the central shaft; the inclined pole shoes are positioned on a plane parallel to the central shaft and form an inclination angle beta with the longitudinal direction, and the inclined pole shoes on the two sides are arrayed at an angle of 180 degrees vertical to the central shaft; the inclined pole shoe is in magnetic conduction with the first connecting rod and the outer rotor coil 19;
the inner rotor 7 is rotatably arranged between the two side inclined pole shoes of the outer rotor 6, the inner rotor 7 comprises a second connecting rod perpendicular to the central shaft, and the second connecting rod is arranged at one end of the valve core 12; two sides of the inner rotor 7 are respectively provided with an inclined plane groove which is positioned on a plane parallel to the central shaft and forms an inclination angle beta with the longitudinal direction; the inclined plane grooves on the two sides are characterized in that the inclined plane grooves are arrayed at an angle of 180 degrees and are vertical to the central shaft, and the inner rotor magnetic sheets 8 are arranged in the inclined plane grooves;
the inclined plane of the inclined plane pole shoe and the inclined plane groove on the same side are parallel to each other, the inner side of the inclined plane pole shoe is opposite to the outer side of the inclined plane groove, the inclined plane pole shoe and the inner rotor magnetic sheet 8 are arranged in a mode that different magnetic surfaces are opposite, the opposite surface of the inclined plane pole shoe and the inner rotor magnetic sheet 8 is a concentric cylindrical cambered surface, and an arc-shaped air gap between the inclined plane pole shoe and the inner rotor magnetic sheet 8 forms a working air gap for driving the valve element 12 to rotate;
the two-dimensional (2D) half-bridge type reversing valve body is a 2D valve consisting of a 2D valve core 11 and a cartridge valve body 12, a threaded end cover 9 is installed at one end of the cartridge valve body 12, and the other end of the cartridge valve body is sealed through a cylindrical plug 13. The 2D spool 11 is rotatably and axially movably disposed in an internal bore of the cartridge valve body 12. The inner hole of the valve body 12 of the cartridge valve is sequentially provided with a T port, an A port, a P port, a B port and a T port, wherein the P port is an oil inlet, and the pressure is the system pressure. The middle part of the 2D valve core 11 is provided with a high-pressure hole B and two shoulders, and the two shoulders in the middle part are respectively positioned above the port A and the port B. In addition, a left high-pressure circular hole a and a right high-pressure rectangular groove c which are communicated with the port P are formed in the 2D valve core 11, and a right low-pressure rectangular groove D which is communicated with the port T is formed in the 2D valve core. And a right sensing channel g communicated with the right sensitive cavity f is formed on the right inner hole wall of the cartridge valve body 12. The right high-pressure rectangular groove c, the right low-pressure rectangular groove d and the T port form a hydraulic resistance bridge. The hydraulic resistance bridge controls the pressure of the sensitive cavities f on the right two sides of the 2D valve core 11. The left high-pressure cavity e is a closed cavity formed by the concentric ring 10 and a second shoulder at the left end of the 2D valve core 11, and the right sensitive cavity f is a closed cavity formed by the cylindrical plug 13 and the right end of the 2D valve core 11.
Preferably, the force-bearing area of the left high-pressure cavity e is 1/2 of the right sensitive cavity f.
The longitudinal direction in the present invention means a direction parallel to the central axis, the coaxial direction in the present invention means a common central axis, the outer direction in the present invention means a side of the member away from the central axis, the inner direction means a side of the member close to the central axis, the coaxial direction means that the longitudinal central axes are on the same straight line, the forward direction means a direction along the output of the linear electromechanical transducer 1 on the central axis, and the reverse direction means a direction opposite to the above-mentioned forward direction.
Two sides of the electric excitation type outer rotor 6 are respectively provided with an inclined pole shoe, and the two inclined pole shoes are arrayed in an array manner of being vertical to the central shaft of the electric excitation type outer rotor 6 by 180 degrees. Two sides of the inner rotor 7 are respectively provided with an inclined plane groove for mounting the inner rotor magnetic sheet 8, and the inclined plane groove of the inner rotor 7 is parallel to the inclined plane pole shoe inclined plane of the electric excitation type outer rotor 6. The inner rotor 7 is fixedly connected with the 2D valve core 11. The inner mover magnetic sheet 8 and the inclined pole shoe of the electrically-excited outer mover 6 are installed to face each other with a different magnetic surface, and the inner mover 7 and the electrically-excited outer mover 6 are positioned on the same plane by the magnetic attraction. The opposite surfaces of the inclined pole shoe of the electrically excited outer rotor 6 and the inner rotor magnetic sheet 8 are respectively a concentric cylindrical cambered surface, the radius R2 of the cylindrical cambered surface of the inclined pole shoe of the electrically excited outer rotor 6 is larger than the radius R1 of the cylindrical cambered surface of the inner rotor magnetic sheet 8, and the geometric relationship enables the annular air gap (air gap R2-R1) between the outer rotor magnetic sheet 18 and the inner rotor magnetic sheet 8 to be reduced to be very small (the air gap can approach zero under the theoretical condition). After the coil 19 is charged, the inclined pole shoe of the outer rotor 6 is excited (the current direction of the coil 19 is shown in a cross section of B-B in (d) of FIG. 9), the size of the air gap has a great influence on the magnetic force, and the smaller the air gap is, the larger the magnetic force is, and the exponential relationship is formed. The inclined pole shoe of the outer rotor 6 and the inclined groove of the inner rotor 7 have the same inclination angle beta and are both characterized in that the inclined pole shoe and the inclined groove are arrayed by 180 degrees and are vertical to the central shaft of the outer rotor 6, and the inner rotor 7 is rotatably arranged in the middle of the outer rotor 6 and can rotate for a certain angle.
The left end cover 2, the right end cover base 5, the left spring seat 16, the spring 17 and the right spring seat 18 form a spring return mechanism. The spring 17 is mounted between the left spring seat 16 and the right spring seat 18. A left spring seat 16 and a right spring seat 18 are installed between the left end cap 2 and the right end cap base 5 to be horizontally linearly movable. The left end cover 2 and the right end cover base 5 are fixedly connected, and the spring 17, the left spring seat 16 and the right spring seat 18 are sealed. The right end cover base 5 is connected with a threaded end cover 9. In addition, the push rod of the linear electro-mechanical transducer 1 is in threaded connection with the threaded connecting rod 15, the shoulder of the threaded connecting rod 15 is attached to the left spring seat 16, the threaded connecting rod 15 is in threaded connection with the push rod 3, the plane of the push rod 3 is attached to the right spring seat 18, and the push plate 3 is connected to the electrically excited outer mover 6. When the linear electromechanical transducer 1 moves in the forward direction, the threaded connecting rod 15 pushes the left spring seat 16 to move in the forward direction. Meanwhile, the threaded connecting rod 15 also pushes the electrically excited outer rotor 6 and the push rod 3 to move forward. This action causes the spring 17 to be compressed. When the linear electro-mechanical converter 1 in the power-on state is powered off, the spring 17 enables the left spring seat 16 to move in the direction, and the left spring seat 16 pulls the threaded connecting rod 15, the electrically-excited outer rotor 6 and the push rod 3 to move in the opposite direction. The above actions make the spring 17 return to the original state, the threaded connecting rod 15, the electrically excited outer rotor 6 and the push rod 3 return to the original position again, the right spring seat 18 is attached to the right end cover base 5, and the left spring seat 16 is attached to the left end cover 2. When the linear electro-mechanical converter 1 is moved in reverse, the threaded connection rod 15 pulls the electrically excited outer mover 6 and the push rod 3 to move in reverse. At the same time, the push rod 3 pushes the right spring seat 18 to move reversely. This action causes the spring 17 to be compressed. When the linear electro-mechanical converter 1 in the power-on state is powered off, the spring 17 makes the right spring seat 18 move in the forward direction, and the right spring seat 18 pushes the threaded connecting rod 15, the electrically-excited outer rotor 6 and the push rod 3 to move in the forward direction. The above actions make the spring 17 return to the original state, the threaded connecting rod 15, the electrically excited outer rotor 6 and the push rod 3 return to the original position again, the right spring seat 18 is attached to the right end cover base 5, and the left spring seat 16 is attached to the left end cover 2. The direct-acting linear electro-mechanical converter mainly realizes the conversion of the output force and the displacement of the direct-acting linear electro-mechanical converter 1 and plays a role in eliminating clearance and zero centering (when the direct-acting linear electro-mechanical converter 1 is not electrified, a pilot control bridge circuit is in rotating centering, and an axial opening of a main valve is in a zero centering state).
The invention has the following beneficial effects:
1. the invention designs an electrically-excited two-dimensional half-bridge servo proportional valve, wherein the opposite working surfaces of the inclined pole shoe of an electrically-excited outer rotor 6 and the inner rotor magnetic sheet 8 are respectively a concentric cylindrical cambered surface (as shown in fig. 9 (a)). The annular air gap design can reduce the air gap between the working surfaces to almost zero. (Objective physics: the magnitude of magnetic force increases exponentially as the working air gap decreases.) in this scheme, a smaller magnetic piece is used to generate a larger torque. This results in a significant increase in the power-to-weight ratio of the overall valve while simplifying construction and reducing cost.
2. According to the electric excitation type two-dimensional half-bridge servo proportional valve designed by the invention, on the premise that the electric excitation type outer rotor 6 does not reach magnetic saturation, the control magnetic flux of the inclined surface pole shoe of the electric excitation type outer rotor 6 can be controlled by changing the current of the coil 19, stepless regulation and control are carried out, the electric excitation type two-dimensional half-bridge servo proportional valve is suitable for more working conditions, and the flexibility is improved.
3. The electrically excited two-dimensional half-bridge servo proportional valve designed by the invention has the advantages that the electrically excited annular air gap magnetic suspension coupling joint innovatively uses a non-contact type force transfer scheme of a magnetic pole with opposite polarities. Because the input force is transferred to the valve core by the attraction magnetic force without contact, the whole motion process has no friction, no abrasion, high speed and high precision, and the influence caused by static characteristics such as linearity, repeatability, hysteresis loop and the like of the valve is fundamentally avoided.
4. The electric excitation type annular air gap magnetic suspension coupling of the single electric excitation type two-dimensional half-bridge servo proportional valve can realize pressure-torsion amplification, namely, the axial thrust generated by a voice coil motor is converted into tangential force to be amplified, and the single electric excitation type two-dimensional half-bridge servo proportional valve is connected with a two-dimensional (2D) half-bridge reversing valve body for use, so that the function of proportional control can be realized.
5. The invention relates to an electrically excited two-dimensional half-bridge servo proportional valve, wherein a two-dimensional (2D) half-bridge reversing valve body is designed into a cartridge valve. This makes the whole invention have high circulation ability, high modularization, high automation etc. advantage.
6. The electric excitation type two-dimensional half-bridge servo proportional valve designed by the invention adopts a two-dimensional flow amplifying mechanism with two degrees of freedom of the valve core, integrates the pilot control stage and the power stage on a single valve core, simplifies the structure, reduces the processing cost and simultaneously greatly improves the power-weight ratio.
Drawings
FIG. 1 is an assembly schematic of the present invention;
FIG. 2 is a schematic of the three-dimensional modeling of the present invention;
FIG. 3 is an assembled schematic view of the electrically excited annular air gap magnetic levitation coupling (including the spring return mechanism) of the present invention;
FIG. 4 is an isometric view of the right end cap base 5 of the present invention;
FIG. 5 is a schematic view of the assembly of the electrically excited outer rotor 6 and the inner rotor 7 of the electrically excited annular air gap magnetic levitation coupling of the present invention;
fig. 6 is a schematic construction of an electrically excited outer mover 6 of the present invention;
fig. 7 is a schematic structural view of the inner mover 7 of the present invention;
fig. 8(a) to 8(c) are three views of an inner mover magnetic sheet 8 of the present invention, fig. 8(a) is a front view, fig. 8(b) is a left view, and fig. 8(c) is a plan view;
FIGS. 9(a) -9 (d) are three views of the electrically excited annular air-gap magnetic levitation coupling of the present invention, including the air-gap schematic, equivalent magnetic circuit and coil current direction, FIG. 9(a) is a front view, FIG. 9(B) is a left side view, FIG. 9(c) is a top view (dotted line in the figure is the magnetic circuit, arrow is the direction of the magnetic circuit), and FIG. 9(d) is a B-B cross-sectional view of FIG. 9 (c);
fig. 10a to 10e are schematic diagrams illustrating decomposition of driving force and motion of an electrically excited two-dimensional half-bridge servo proportional valve according to the present invention, in which fig. 10a is a schematic diagram illustrating an initial balanced state of the electrically excited two-dimensional half-bridge servo proportional valve, fig. 10b is a schematic diagram illustrating a position shift of an electrically excited outer mover 6 and an inner mover magnetic sheet 8 due to an output force of a voice coil motor, fig. 10c is a schematic diagram illustrating a position shift of an inner mover 7 of the electrically excited two-dimensional half-bridge servo proportional valve due to a torque generated by a position shift of an electrically excited outer mover 6 inclined surface pole piece and the inner mover magnetic sheet 8, fig. 10D is a schematic diagram illustrating an axial displacement of a 2D spool 11 of the electrically excited two-dimensional half-bridge servo proportional valve due to a pressure difference between a sensitive chamber f and a high pressure chamber e, and fig. 10e is a schematic diagram illustrating a position shift of the inner mover 7 of the electrically excited two-dimensional half-bridge servo proportional valve due to a torque generated by a position shift of Schematic illustration of
Detailed Description
The invention is further described below with reference to the accompanying drawings.
As shown in fig. 1 to 10, the electrically-excited two-dimensional half-bridge servo proportional valve comprises a two-dimensional (2D) half-bridge reversing valve body, a direct-acting linear electro-mechanical converter 1 and an electrically-excited annular air gap magnetic suspension coupling.
The two-dimensional (2D) half-bridge type reversing valve body is a 2D valve consisting of a 2D valve core 11 and a cartridge valve body 12, a threaded end cover 9 is installed at one end of the cartridge valve body 12, and the other end of the cartridge valve body is sealed through a cylindrical plug 13. The 2D spool 11 is rotatably and axially movably disposed in an internal bore of the cartridge valve body 12. The inner hole of the valve body 12 of the cartridge valve is sequentially provided with a T port, an A port, a P port, a B port and a T port, wherein the P port is an oil inlet, and the pressure is the system pressure. The middle part of the 2D valve core 11 is provided with a high-pressure hole B and two shoulders, and the two shoulders in the middle part are respectively positioned above the port A and the port B. In addition, a left high-pressure circular hole a and a right high-pressure rectangular groove c which are communicated with the port P are formed in the 2D valve core 11, and a right low-pressure rectangular groove D which is communicated with the port T is formed in the 2D valve core. And a right sensing channel g communicated with the right sensitive cavity f is formed on the right inner hole wall of the cartridge valve body 12. The right high-pressure rectangular groove c, the right low-pressure rectangular groove d and the T port form a hydraulic resistance bridge. The hydraulic resistance bridge controls the pressure of the sensitive cavities f on the right two sides of the 2D valve core 11. The left high-pressure cavity e is a closed cavity formed by the concentric ring 10 and a second shoulder at the left end of the 2D valve core 11, and the right sensitive cavity f is a closed cavity formed by the cylindrical plug 13 and the right end of the 2D valve core 11. The force-bearing area of the left high-pressure chamber e is 1/2 of the right sensitive chamber f.
The electric excitation type annular air gap magnetic suspension coupling body comprises a left end cover 2, a push plate 3, a linear bearing 4, a right end cover base 5, an electric excitation type outer rotor 6, an inner rotor 7, an inner rotor magnetic sheet 8, a threaded connecting rod 15, a left spring seat 16, a spring 17, a right spring seat 18 and an outer rotor coil 19, wherein the push plate 3 and the electric excitation type outer rotor 6 are in interference fit, and in order to enable the electric excitation type outer rotor 6 to only do horizontal linear motion, the linear bearing 4 is sleeved on a cylinder of the push plate 3 and is installed on the right end cover base 5. As shown in fig. 6, two sides of the electrically excited outer rotor 6 are respectively provided with an inclined pole shoe, and the inclined pole shoes are all characterized in that the inclined pole shoes are arrayed at 180 degrees and perpendicular to a central axis (a front view plane, an intersecting plane of an upper view plane and a right view plane) of the electrically excited outer rotor 6. Two sides of the inner rotor 7 are respectively provided with an inclined plane groove for mounting the inner rotor magnetic sheet 8, and the inclined plane groove of the inner rotor 7 is parallel to the inclined plane pole shoe inclined plane of the electric excitation type outer rotor 6. The inner rotor 7 is fixedly connected with the 2D valve core 11. The inner mover magnetic sheet 8 and the slant pole piece of the electrically-excited outer mover 6 are installed to face each other with different magnetic surfaces (as shown in fig. 5), and the inner mover 7 and the electrically-excited outer mover 6 are positioned on the same plane by the magnetic attractive force (as shown in fig. 9 (c)). As shown in fig. 9(a), the surfaces of the electrically excited outer rotor 6, which are opposite to the inner rotor magnetic sheet 8, are concentric cylindrical arc surfaces, and the radius R2 of the cylindrical arc surface of the electrically excited outer rotor 6, which is larger than the radius R1 of the cylindrical arc surface of the inner rotor magnetic sheet 8, so that the annular air gap (air gap R2-R1) between the outer rotor magnetic sheet 18 and the inner rotor magnetic sheet 8 can be reduced to be very small (the air gap can approach to zero in the theoretical case). The coil 19 is charged to excite the inclined pole shoe of the electrically excited outer mover 6 (the current direction of the coil 19 is shown in the sectional view of fig. 9(d) B-B), the air gap size has a large influence on the magnetic force, and the smaller the air gap is, the larger the magnetic force is, and the exponential relationship is formed. The inclined pole shoe of the outer rotor 6 and the inclined groove of the inner rotor 7 have the same inclination angle beta and are both characterized in that the inclined pole shoe and the inclined groove are arrayed by 180 degrees and are vertical to the central shaft of the outer rotor 6, and the inner rotor 7 is rotatably arranged in the middle of the outer rotor 6 and can rotate for a certain angle.
In addition, the left end cover 2, the right end cover base 5, the left spring seat 16, the spring 17 and the right spring seat 18 form a spring return mechanism (as shown in fig. 3). The spring 17 is mounted between the left spring seat 16 and the right spring seat 18. A left spring seat 16 and a right spring seat 18 are installed between the left end cap 2 and the right end cap base 5 to be horizontally linearly movable. The left end cover 2 and the right end cover base 5 are fixedly connected through hexagon socket head cap screws, and the spring 17, the left spring seat 16 and the right spring seat 18 are sealed. The right end cover base 5 is connected with the threaded end cover 9 through an inner hexagon screw. In addition, the push rod of the linear electro-mechanical converter 1 is in threaded connection with the threaded connecting rod 15, the shoulder of the threaded connecting rod 15 is attached to the left spring seat 16, the threaded connecting rod 15 is in threaded connection with the push rod 3, the plane of the push rod 3 is attached to the right spring seat 18, and the push plate 3 is in interference fit with the electrically-excited outer rotor 6. When the linear electro-mechanical converter 1 moves to the right, the threaded connecting rod 15 pushes the left spring seat 16 to move to the right. At the same time, the threaded connecting rod 15 also pushes the electrically excited outer mover 6 and the push rod 3 to move to the right. This action causes the spring 17 to be compressed. When the linear electro-mechanical converter 1 in the power-on state is powered off, the spring 17 makes the left spring seat 16 move leftward, and the left spring seat 16 pulls the threaded connection rod 15, the electrically-excited outer mover 6 and the push rod 3 to move leftward. The above actions make the spring 17 return to the original state, the threaded connecting rod 15, the electrically excited outer rotor 6 and the push rod 3 return to the original position again, the right spring seat 18 is attached to the right end cover base 5, and the left spring seat 16 is attached to the left end cover 2. When the linear electro-mechanical converter 1 moves leftward, the threaded connection rod 15 pulls the electrically excited outer mover 6 and the push rod 3 to move leftward. At the same time, the push rod 3 pushes the right spring seat 18 to move leftward. This action causes the spring 17 to be compressed. When the linear electro-mechanical converter 1 in the power-on state is powered off, the spring 17 makes the right spring seat 18 move rightwards, and the right spring seat 18 pushes the threaded connecting rod 15, the electrically-excited outer rotor 6 and the push rod 3 to move rightwards. The above actions make the spring 17 return to the original state, the threaded connecting rod 15, the electrically excited outer rotor 6 and the push rod 3 return to the original position again, the right spring seat 18 is attached to the right end cover base 5, and the left spring seat 16 is attached to the left end cover 2. The direct-acting linear electro-mechanical converter mainly realizes the conversion of the output force and the displacement of the direct-acting linear electro-mechanical converter 1 and plays a role in eliminating clearance and zero centering (when the direct-acting linear electro-mechanical converter 1 is not electrified, a pilot control bridge circuit is in rotating centering, and an axial opening of a main valve is in a zero centering state).
The linear electro-mechanical converter 1 of the electric excitation type two-dimensional half-bridge servo proportional valve is a commercial product which is mature in the market at present, and the electric excitation type annular air gap magnetic suspension coupling is mainly used for converting axial thrust generated by the linear electro-mechanical converter 1 into tangential force, amplifying the tangential force and driving the 2D valve core 11 to rotate, so that the rotating angle is within +/-3 degrees, and the translational displacement is within +/-2 mm.
The operation principle of the present invention is broken down as shown in fig. 10(a), 10(b), 10(c), 10(d), and 10(e), and in particular, the operation states of fig. 10(a), 10(b), 10(c), 10(d), and 10(e) are continuously performed at the same time. Firstly, the valve core stress area of the e end of the left sensitive cavity is half of that of the f end of the right sensitive cavity. First, the electrically excited two-dimensional half-bridge servo proportional valve is zeroed and the coil 19 is energized. As shown in fig. 10(a), when none of the direct-acting linear electro-mechanical converters 1 of the electrically-excited two-dimensional half-bridge servo proportional valve is energized, the oil pressure of the left sensitive chamber e is twice that of the right sensitive chamber f (in order to keep the force balance of the valve core, since the force-bearing area of the left high-pressure chamber e is 1/2 of the right sensitive chamber f). The oil pressure of the right sensitive cavity f is obtained by adjusting a hydraulic resistance bridge formed by the right high-pressure rectangular groove c, the right low-pressure rectangular groove d and the T port. Meanwhile, because the inner rotor 7 and the electrically-excited outer rotor 6 are in an initial balance position, the two magnetic sheets are stabilized on the same plane by magnetic attraction force generated by the inclined pole shoe of the electrically-excited outer rotor 6 and the inner rotor magnetic sheet 8. At this time, the port A, the port B, the port P and the port T are not communicated with each other. Referring to FIG. 10(b), when the linear electro-mechanical converter 1 at the left end of the electrically excited two-dimensional half-bridge servo proportional valve is energized, it moves xiWhen it is in use, it generates electromagnetic thrust to the right to move the electrically excited outer mover 6 horizontally to the right xi. Due to the right movement of the electrically excited outer rotor 6, the inclined pole shoe of the electrically excited outer rotor 6 and the inner rotor magnetic sheet 8 are dislocated. Magnetic attraction between the inclined pole shoe of the outer rotor 6 and the inner rotor magnetic sheet 8 caused by dislocationF(F1The inner rotor magnetic sheet 8 is subject to the magnetic attraction of the inclined pole shoe of the electric excitation type outer rotor 6, F2The inclined pole shoe of the electric excitation type outer rotor 6 is subject to the magnetic attraction of the inner rotor magnetic sheet 8, F1And F2Equal in magnitude and opposite in direction) will generate a tangential component Fy(F1yThe inner rotor magnetic sheet 8 is subjected to a tangential force F generated by the magnetic attraction of the inclined pole shoe of the electrically excited outer rotor 62yThe inclined pole shoe of the electric excitation type outer rotor 6 is subjected to the tangential force of the magnetic attraction force generated by the inner rotor magnetic sheet 8, F1yAnd F2yEqual in size and opposite in direction). The inner rotor 7 is subjected to a tangential force F1yA counterclockwise torque (a counterclockwise torque with a view angle perpendicular to the right end face of the spool) is formed. The inner rotor 7 will drive the 2D valve core 11 to rotate counterclockwise. As shown in fig. 10(c), after the 2D valve core 11 rotates counterclockwise by a certain angle, the right low-pressure rectangular groove D communicates with the right sensing channel g, so that the oil pressure of the right sensing chamber f is much smaller than that of the left high-pressure chamber e. This pressure differential causes the 2D spool 11 to experience an axial force to the right. This axial force will drive the 2D spool to move horizontally to the right. As shown in FIG. 10(D), the 2D spool translates x to the rightoThen, the port P is communicated with the port B, and the port T is communicated with the port A. At this time, the inclined pole shoe of the electrically excited outer mover 6 and the inner mover magnetic sheet 8 are misaligned. The magnetic attraction force F (F) between the inclined pole shoe of the electric excitation type outer rotor 6 and the inner rotor magnetic sheet 8 is caused by dislocation4The inner rotor magnetic sheet 8 is subject to the magnetic attraction of the inclined pole shoe of the electric excitation type outer rotor 6, F3The inclined pole shoe of the electric excitation type outer rotor 6 is subject to the magnetic attraction of the inner rotor magnetic sheet 8, F3And F4Equal in magnitude and opposite in direction) will generate a tangential component Fy(F4yThe inner rotor magnetic sheet 8 is subjected to a tangential force F generated by the magnetic attraction of the inclined pole shoe of the electrically excited outer rotor 63yThe inclined pole shoe of the electric excitation type outer rotor 6 is subjected to the tangential force of the magnetic attraction force generated by the inner rotor magnetic sheet 8, F3yAnd F4yEqual in size and opposite in direction). The inner rotor 7 is subjected to a tangential force F4yA clockwise torque is formed (clockwise torque with the viewing angle perpendicular to the right end face of the spool). The inner rotor 7 will drive the 2D valve element 11 to rotate clockwise. As shown in the figure10(e), the 2D spool 11 rotates clockwise by a certain angle, so that the inner rotor 7 and the electrically-excited outer rotor 6 return to the initial balance position, and the magnetic attraction force generated by the outer rotor magnetic sheet 18 and the inner rotor magnetic sheet 8 stabilizes the two magnetic sheets on the same plane. The whole electrically excited two-dimensional half-bridge servo proportional valve does not move any more and keeps stable work. The opposite is true when the linear electro-mechanical transducer 1 is moving in reverse. After the direct-acting linear electro-mechanical converter 1 of the electric excitation type two-dimensional half-bridge servo proportional valve is powered off, the direct-acting linear electro-mechanical converter 1 does not generate thrust any more, so that the electric excitation type outer rotor 6 of the electric excitation type annular air gap magnetic suspension coupling horizontally and axially moves in the opposite direction (namely the movement direction is opposite to the movement direction of the electric excitation type outer rotor 6 when the electric excitation type outer rotor 6 is powered on). Due to the movement of the electrically excited outer mover 6, the electrically excited annular air gap magnetic levitation coupling also starts to work, generating a corresponding axial driving force and torque, which returns the 2D spool 11 and the inner mover 7 to the original position. It should be noted that, under the condition that the pressure at the port P of the valve is zero (equal to the pressure at the port T), the pressure of the right-end sensing chamber g cannot be controlled by the two-dimensional reversing valve to drive the valve core to move axially. However, when no oil flows in the valve cavity, the 2D valve core 11 is not affected by hydrodynamic force and clamping force, the 2D valve core 11 can be directly driven by electromagnetic thrust generated by the direct-acting linear electro-mechanical converter 1, and at this time, the working principle of the electrically-excited two-dimensional half-bridge servo proportional valve is consistent with that of the direct-acting proportional valve.
The embodiments described in this specification are merely illustrative of implementations of the inventive concept and the scope of the present invention should not be considered limited to the specific forms set forth in the embodiments but rather by the equivalents thereof as may occur to those skilled in the art upon consideration of the present inventive concept.
Claims (2)
1. Electric excitation formula two dimension half-bridge servo proportional valve, its characterized in that: the two-dimensional (2D) half-bridge reversing valve comprises a direct-acting linear electro-mechanical converter (1), an electrically-excited annular air gap magnetic suspension coupling and a two-dimensional (2D) half-bridge reversing valve body which are coaxially connected in sequence.
The output end of the linear electric-mechanical converter (1) is connected with a threaded connecting rod (15) of the linear electric-mechanical converter (1), the threaded connecting rod (15) is connected with a push plate (3), and the push plate (3) is connected with an outer rotor (6);
the electric excitation type annular air gap magnetic suspension coupling body comprises a left end cover (2) and a right end cover base (5) which are connected with each other; a left spring seat (16) and a right spring seat (18) are sleeved on the threaded connecting rod (15), a spring (17) is arranged between the left spring seat (16) and the right spring seat (18), and the axial positions of the left spring seat (16) and the right spring seat (18) are limited by a left end cover (2) and a right end cover base (5) respectively; in order to enable the electric excitation type outer rotor (6) to only do longitudinal motion, the linear bearing (4) is sleeved on the cylinder of the push plate (3) and is arranged on the right end cover base (5).
The outer rotor (6) is approximately U-shaped, two sides of the first connecting rod are respectively connected with an inclined pole shoe, the first connecting rod is vertical to the central shaft, and an outer rotor coil (19) arranged on the first connecting rod is positioned on the central shaft; the inclined pole shoes are positioned on a plane parallel to the central shaft and form an inclination angle beta with the longitudinal direction, and the inclined pole shoes on the two sides are arrayed at an angle of 180 degrees vertical to the central shaft; the inclined pole shoe is in magnetic conduction with the first connecting rod and the outer rotor coil (19);
the inner rotor (7) is rotatably arranged between the inclined pole shoes at the two sides of the outer rotor (6), the inner rotor (7) comprises a second connecting rod perpendicular to the central shaft, and the second connecting rod is arranged at one end of the valve core (12); two sides of the inner rotor (7) are respectively provided with an inclined plane groove, and the inclined plane grooves are positioned on a plane parallel to the central shaft and form an inclined angle beta with the longitudinal direction; the inclined plane grooves on the two sides are characterized in that the inclined plane grooves are arrayed at an angle of 180 degrees and are vertical to the central shaft, and inner rotor magnetic sheets (8) are arranged in the inclined plane grooves;
the inclined plane of the inclined plane pole shoe and the inclined plane groove on the same side are parallel to each other, the inner side of the inclined plane pole shoe is opposite to the outer side of the inclined plane groove, the inclined plane pole shoe and the inner rotor magnetic sheet (8) are arranged in a mode that different magnetic surfaces are opposite, the opposite surface of the inclined plane pole shoe and the inner rotor magnetic sheet (8) is a concentric cylindrical cambered surface, and an arc-shaped air gap between the inclined plane pole shoe and the inner rotor magnetic sheet (8) forms a working air gap for driving the valve core (12) to rotate;
the two-dimensional (2D) half-bridge type reversing valve body is a 2D valve consisting of a 2D valve core (11) and a cartridge valve body (12), a threaded end cover (9) is installed at one end of the cartridge valve body (12), and the other end of the cartridge valve body is sealed through a cylindrical plug (13). The 2D valve core (11) is rotatably and axially movably arranged in an inner hole of the valve body (12) of the cartridge valve. An inner hole of the valve body (12) of the cartridge valve is sequentially provided with a T port, an A port, a P port, a B port and a T port, wherein the P port is an oil inlet, and the pressure is the system pressure. The middle part of the 2D valve core (11) is provided with a high-pressure hole B and two shoulders, and the two middle shoulders are respectively positioned above the port A and the port B. In addition, a left high-pressure circular hole a and a right high-pressure rectangular groove c which are communicated with the port P are formed in the 2D valve core (11), and a right low-pressure rectangular groove D which is communicated with the port T is formed in the 2D valve core. And a right sensing channel g communicated with the right sensitive cavity f is formed on the right inner hole wall of the cartridge valve body (12). The right high-pressure rectangular groove c, the right low-pressure rectangular groove d and the T port form a hydraulic resistance bridge. The hydraulic resistance bridge controls the pressure of the sensitive cavities f on the right two sides of the 2D valve core (11). The left high-pressure cavity e is a closed cavity formed by a concentric ring (10) and a second shoulder at the left end of the 2D valve core (11), and the right sensitive cavity f is a closed cavity formed by a cylindrical plug (13) and the right end of the 2D valve core (11).
The longitudinal direction is a direction parallel to the central axis, the outer side is a side of the component far from the central axis, the inner side is a side of the component close to the central axis, the coaxial directions are that the longitudinal central axes are on the same straight line, the forward direction is a direction along the output of the linear electromechanical transducer (1) on the central axis, and the reverse direction is a direction opposite to the forward direction.
2. An electrically excited two-dimensional half-bridge servo proportional valve as claimed in claim 1, wherein: the force-bearing area of the left high-pressure chamber e is 1/2 of the right sensitive chamber f.
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1323966A1 (en) * | 2001-12-21 | 2003-07-02 | G. Kromschröder Aktiengesellschaft | Device and method for controlling and cutting off a fluid flow |
| KR20050005837A (en) * | 2003-07-07 | 2005-01-15 | 엘지전자 주식회사 | Fluidic mass flow control valve actuated by electromagnetic force |
| CN110617246A (en) * | 2018-09-17 | 2019-12-27 | 浙江工业大学 | Two-dimensional half-bridge type electro-hydraulic proportional reversing valve based on Halbach array bidirectional magnetic suspension coupling |
| CN110994932A (en) * | 2019-12-13 | 2020-04-10 | 浙江工业大学 | High-frequency direct-acting type force motor based on mixed air gap |
| CN111140562A (en) * | 2019-12-25 | 2020-05-12 | 浙江工业大学 | Plug-in type two-dimensional magnetic suspension servo proportional valve with static pressure support |
| CN212899208U (en) * | 2020-08-12 | 2021-04-06 | 浙江工业大学 | Electric excitation type two-dimensional half-bridge servo proportional valve |
-
2020
- 2020-09-07 CN CN202010928699.3A patent/CN112065796B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1323966A1 (en) * | 2001-12-21 | 2003-07-02 | G. Kromschröder Aktiengesellschaft | Device and method for controlling and cutting off a fluid flow |
| KR20050005837A (en) * | 2003-07-07 | 2005-01-15 | 엘지전자 주식회사 | Fluidic mass flow control valve actuated by electromagnetic force |
| CN110617246A (en) * | 2018-09-17 | 2019-12-27 | 浙江工业大学 | Two-dimensional half-bridge type electro-hydraulic proportional reversing valve based on Halbach array bidirectional magnetic suspension coupling |
| CN110994932A (en) * | 2019-12-13 | 2020-04-10 | 浙江工业大学 | High-frequency direct-acting type force motor based on mixed air gap |
| CN111140562A (en) * | 2019-12-25 | 2020-05-12 | 浙江工业大学 | Plug-in type two-dimensional magnetic suspension servo proportional valve with static pressure support |
| CN212899208U (en) * | 2020-08-12 | 2021-04-06 | 浙江工业大学 | Electric excitation type two-dimensional half-bridge servo proportional valve |
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