CN212899208U

CN212899208U - Electric excitation type two-dimensional half-bridge servo proportional valve

Info

Publication number: CN212899208U
Application number: CN202021935609.5U
Authority: CN
Inventors: 孟彬; 刘备; 徐豪; 朱晨航; 戴铭柱
Original assignee: Zhejiang University of Technology ZJUT
Current assignee: Zhejiang University of Technology ZJUT
Priority date: 2020-08-12
Filing date: 2020-09-07
Publication date: 2021-04-06
Anticipated expiration: 2030-09-07

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 utility model discloses can reduce the working air gap, use littleer magnetic sheet to produce great torque promptly.

Description

Electric excitation type two-dimensional half-bridge servo proportional valve

Technical Field

The utility model belongs to flow and switching-over control valve that electro-hydraulic proportional control technique used in fluid drive and control field especially relate to an electric excitation formula two dimension 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 half-bridge servo proportional valve has +/-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. A valve body of the magnetic suspension coupling type two-dimensional half-bridge 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 utility model discloses solve the problem that exists in the servo proportional valve of current magnetic suspension shaft coupling formula electricity liquid: 1. the magnetic suspension coupling cannot achieve a very small working air gap; 2. the valve body is plate valve body, leads to its circulation ability not high, the modularization degree is low, degree of automation is low not enough, the utility model provides an electricity excitation formula two-dimensional half-bridge servo proportional valve.

The utility model discloses an electric excitation formula two-dimensional half-bridge servo proportional valve, including coaxial coupling's two-dimensional (2D) half-bridge type switching-over valve body, electric excitation formula annular air gap magnetic suspension shaft coupling and the linear electricity of direct action-mechanical converter 1 in proper order.

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 in 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 arrayed in an angle of 180 degrees 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.

Vertical direction be parallel with the center pin, coaxial be the center pin altogether, the utility model discloses the outside of saying indicates the one side of keeping away from the center pin of part, the inboard is one side that is close to the center pin of part, coaxial be the vertical center pin on same straight line, forward is the direction of the output of following the linear electricity of direct action-mechanical converter 1 on the center pin, reverse is the opposite direction of above-mentioned forward.

Two sides of the electric excitation type outer rotor 6 are respectively provided with an inclined pole shoe, and the inclined pole shoes are arrayed in an array of 180 degrees vertical to the central shaft of the electric excitation type 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 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 electrically excited outer rotor 6 and the inclined groove of the inner rotor 7 have the same inclination angle beta and are arrayed in an array of 180 degrees perpendicular to the central shaft of the electrically excited outer rotor 6, and the inner rotor 7 is rotatably arranged in the middle of the electrically excited 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 enables the right spring seat 18 to 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 beneficial effects of the utility model are that:

1. the utility model relates to an electrically excited magnetic two-dimensional half-bridge servo proportional valve, wherein the inclined plane pole shoe of outer active cell 6 of electrically excited magnetic and the relative working face of interior active cell magnetic sheet 8 are a concentric cylinder cambered surface respectively (as figure 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. The utility model discloses an electrically excited magnetic two-dimensional half-bridge servo proportional valve under the prerequisite that the outer active cell 6 of electrically excited magnetic did not reach magnetic saturation, can control the control magnetic flux of the outer active cell 6 inclined plane pole shoes of electrically excited magnetic through the electric current size that changes coil 19, carries out stepless regulation and control, adaptable more operating modes, and the flexibility improves.

3. The utility model discloses an electric excitation formula two dimension half-bridge servo proportional valve, its electric excitation formula annular air gap magnetic suspension coupling joint have used the power transmission scheme of non-contact opposite magnetic pole innovatively. 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 utility model discloses a single electric excitation formula two dimension half-bridge servo proportional valve, its electric excitation formula annular air gap magnetic suspension shaft coupling can realize pressing to turn round and enlarge, is about to the tangential force that produced axial thrust of voice coil motor converted and enlargies, uses with this body coupling of two dimension (2D) half-bridge formula switching-over valve, can realize proportional control's function.

5. The utility model discloses an electric excitation formula two dimension half-bridge servo proportional valve, its two dimension (2D) half-bridge formula switching-over valve body is designed into the cartridge valve. This makes the whole invention have high circulation ability, high modularization, high automation etc. advantage.

6. The utility model discloses an electric excitation formula two dimension half-bridge servo proportional valve adopts the two-dimensional flow mechanism of enlargiing of case two degrees of freedom, will lead accuse level and power level integration on single case, improved power weight ratio greatly when simplifying the structure, reducing the processing cost.

Drawings

FIG. 1 is a schematic assembly view of the present invention;

FIG. 2 is a schematic of the three-dimensional modeling of the present invention;

FIG. 3 is an assembly schematic diagram of an electrically excited circular air gap magnetic levitation coupling (including a spring return mechanism) of the present invention;

fig. 4 is an axial side view of the right end cap base 5 of the present invention;

fig. 5 is an assembly schematic diagram of an electrically excited outer rotor 6 and an inner rotor 7 of the electrically excited annular air gap magnetic levitation coupling of the present invention;

fig. 6 is a schematic structural view of an electrically excited outer mover 6 of the present invention;

fig. 7 is a schematic structural diagram of the inner rotor 7 of the present invention;

fig. 8(a) to 8(c) are three views of the inner mover magnetic sheet 8 of the present invention, fig. 8(a) is a front view, fig. 8(b) is a left side view, and fig. 8(c) is a plan view;

fig. 9(a) -9 (d) are three views of the electrically excited ring air gap magnetic suspension coupling of the present invention, including the air gap schematic, the equivalent magnetic circuit and the 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 (the dotted line in the figure is the magnetic circuit, the arrow is the direction of the magnetic circuit), fig. 9(d) is a B-B cross-sectional view of fig. 9 (c);

fig. 10(a) -10 (e) are schematic diagrams illustrating the decomposition of the driving force and the movement of the electrically excited two-dimensional half-bridge servo proportional valve of the present invention, wherein fig. 10(a) is a schematic diagram illustrating an initial equilibrium state of the electrically excited two-dimensional half-bridge servo proportional valve, fig. 10(b) is a schematic diagram illustrating the displacement of the electrically excited outer mover 6 and the inner mover magnetic sheet 8 due to the output force of the voice coil motor, fig. 10(c) is a schematic diagram illustrating the rotation of the 2D valve element 11 due to the torque generated by the displacement of the inner mover 8 and the electrically excited outer mover 6 inclined plane pole piece of the electrically excited two-dimensional half-bridge servo proportional valve, fig. 10(D) is a schematic diagram illustrating the axial displacement of the 2D valve element 11 of the electrically excited two-dimensional half-bridge servo proportional valve due to the pressure difference between the sensitive chamber f and the high pressure chamber e, and fig. 10(e) is a schematic diagram illustrating the displacement of the torque generated by the displacement of the inner mover 8 and the displacement of the And the schematic diagram of driving the 2D valve core 11 to rotate and return to the equilibrium state

Detailed Description

The present invention will be further described 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 arrayed in an angle of 180 ° perpendicular to the central axis (front view plane, intersecting plane of the top view plane and the 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 electrically excited outer rotor 6 and the inclined groove of the inner rotor 7 have the same inclination angle beta and are arrayed in an array of 180 degrees perpendicular to the central shaft of the electrically excited outer rotor 6, and the inner rotor 7 is rotatably arranged in the middle of the electrically excited 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 decomposed as shown in fig. 10(a), 10(b), 10(c), 10(d), and 10(e), and the operation states of fig. 10(a), 10(b), 10(c), 10(d), and 10(e) are continuously performed at the same time during the specific operation. 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 the initial balance position, the magnetic attraction force generated by the inclined pole shoe of the electrically-excited outer rotor 6 and the inner rotor magnetic sheet 8 makes the two magnetsThe sheets are stabilized in the same plane. 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 x_iWhen it is in use, it generates electromagnetic thrust to the right to move the electrically excited outer mover 6 horizontally to the right x_i. 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. 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 dislocation₁The 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 F_y(F_1yThe 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 6_2yThe 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, F_1yAnd F_2yEqual in size and opposite in direction). The inner rotor 7 is subjected to a tangential force F_1yA 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 right_oThen, 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 size and opposite in direction) will yield oneTangential component force F_y(F_4yThe 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 6_3yThe 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, F_3yAnd F_4yEqual in size and opposite in direction). The inner rotor 7 is subjected to a tangential force F_4yA 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 fig. 10(e), the 2D spool 11 rotates clockwise by a certain angle, so that the inner mover 7 and the electrically-excited outer mover 6 return to the initial equilibrium position, and the magnetic attraction force generated by the outer mover magnetic sheet 18 and the inner mover 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 invention should not be considered limited to the specific forms set forth in the embodiments but rather the scope of the invention is intended to cover all technical equivalents that may occur to those skilled in the art based on the inventive concept.

Claims

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 ensure that the electric excitation type outer rotor (6) can 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 in 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; 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 arrayed in an angle of 180 degrees 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 core to rotate;

the two-dimensional (2D) half-bridge reversing valve body is a 2D valve consisting of a 2D valve core (11) and a cartridge valve body (12), one end of the cartridge valve body (12) is provided with a threaded end cover (9), and the other end of the cartridge valve body is sealed by 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; a right sensing channel g communicated with the right sensitive cavity f is formed in the wall of the right inner hole 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 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 part 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 longitudinal central axes on the same straight line, the forward direction is a direction along the output of the linear electro-mechanical converter (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.