CN112984198B - Two-dimensional half-bridge electro-hydraulic proportional reversing valve based on push rod middle-positioned roller coupling - Google Patents
Two-dimensional half-bridge electro-hydraulic proportional reversing valve based on push rod middle-positioned roller coupling Download PDFInfo
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- CN112984198B CN112984198B CN202110274612.XA CN202110274612A CN112984198B CN 112984198 B CN112984198 B CN 112984198B CN 202110274612 A CN202110274612 A CN 202110274612A CN 112984198 B CN112984198 B CN 112984198B
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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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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F16K31/0624—Lift valves
- F16K31/0627—Lift valves with movable valve member positioned between seats
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Abstract
The two-dimensional half-bridge electro-hydraulic proportional reversing valve based on the push rod middle-mounted roller coupling comprises a bidirectional proportional electromagnet, the push rod middle-mounted roller coupling and a 2D half-bridge electro-hydraulic proportional reversing valve body which are sequentially arranged from left to right, wherein the 2D half-bridge electro-hydraulic proportional reversing valve body comprises a valve body, a valve sleeve and a valve core, the bidirectional proportional electromagnet is installed at the left end of the valve body, the push rod middle-mounted roller coupling is installed at the left end of the valve core, and the valve core is connected with the bidirectional proportional electromagnet through the push rod middle-mounted roller coupling. The invention adopts a two-dimensional hydraulic amplifying mechanism with two degrees of freedom of the valve core, takes the rotation of the valve core as a pilot stage, takes the axial movement of the valve core as a power stage, integrates the pilot stage and the power stage on a single valve core, has simple structure and low processing cost, and greatly improves the power-weight ratio.
Description
Technical Field
The invention relates to a directional control valve for an electro-hydraulic proportional control technology in the field of fluid transmission and control, in particular to a two-dimensional half-bridge electro-hydraulic proportional reversing valve based on a push rod middle-positioned roller coupling.
Background
The hydraulic transmission technology has been applied to various cranes and presses for nearly two hundred years since the 50 th century, and at the present stage, the hydraulic technology and the microelectronic technology are combined, the hydraulic technology has made great progress in realizing high efficiency, high power, low noise, high speed, high pressure, high integration, intellectualization and other aspects, is mainly applied to industrial occasions such as military weapons, aerospace, ships and oceans, steel smelting, forging and casting and the like, and even has overwhelming advantages in certain fields, for example, more than 95% of engineering machinery and automatic production lines produced in the world and 90% of numerical control machining centers adopt hydraulic transmission, so that the hydraulic technology becomes one of the standards for measuring the developed degree of the national industry.
In recent years, as the hydraulic technology is combined with the microelectronic technology and the computer technology, and the performance of the hydraulic element is continuously improved and improved, the development of the hydraulic technology is greatly advanced, and more achievements are obtained in the aspects of proportional control, servo control, digital control and the like of a hydraulic system. Since the advent of electro-hydraulic servo technology in the fortieth of the last century, electro-hydraulic servo technology has occupied a high-end position in electromechanical transmission and control due to the characteristics of fast response, large power-weight ratio, high precision and the like. Especially in recent society, the promotion of industrial revolution and the development of the whole industrial technology, mainly in the fields of military weapons and aerospace, promote the rapid development of the electro-hydraulic servo technology, so that the technology is gradually improved and matured in not only the aspects of elements and systems, but also the theoretical aspects. Initially, the electro-hydraulic servo technology was first applied to airplanes, and later, due to the development of electromagnetism, a permanent magnet torque motor and a force motor with fast response appeared to form an electro-hydraulic servo valve. With the development of the industrial society, nozzle flapper valves and jet pipe valves have been followed. After the 60 s in the 19 th century, electro-hydraulic servo valves of various structures appeared in succession, the response speed was improved, the functions were increasingly improved, and the electro-hydraulic servo valves were widely applied to the national defense industry, such as automatic control systems of missiles, steering devices of naval vessels, stabilizing systems of armored tanks, and the like. Meanwhile, the method is widely applied to general mechanical industries such as precision machine tools, engineering machinery, mining machinery and the like.
Although the electro-hydraulic servo valve has good rapidity, high control precision and fast system response, the requirement on the cleanliness of oil is very high, and the requirement on the processing and assembling precision of key parts is also very strict, so that the production cost of the electro-hydraulic servo valve is increased, and people generally hope that a technology which has low processing and manufacturing cost, reliable performance, strong pollution resistance and response characteristic and control precision meeting the actual requirement of a control system can be provided, and the electro-hydraulic proportional technology is developed on the background. The key control element of the electro-hydraulic proportional technology is an electro-hydraulic proportional valve, and the performance of the electro-hydraulic proportional valve is between that of a common hydraulic valve and that of an electro-hydraulic servo valve. The standard of the cleanliness of hydraulic oil required by the electro-hydraulic servo valve needs to reach Nas-3 level, and the electro-hydraulic proportional valve only needs to reach Nas-5 level, so that the anti-pollution performance of the electro-hydraulic servo valve is superior to that of the electro-hydraulic servo valve, and the electro-hydraulic servo valve is simple in structure, low in processing and manufacturing precision requirement and relatively low in price. In modern industry, almost all pressure valves, flow valves and direction valves can find corresponding electro-hydraulic proportional products, and the electro-hydraulic proportional valves are more and more widely applied to industrial production due to the obvious advantages of the electro-hydraulic proportional valves.
The electro-hydraulic proportional valve mainly comprises an electro-hydraulic proportional pressure valve, an electro-hydraulic proportional direction valve and an electro-hydraulic proportional flow valve, and has the common point that a proportional electro-mechanical converter, namely a proportional electromagnet (force motor), plays a key control role. The electro-hydraulic proportional directional valve mainly refers to an electro-hydraulic proportional reversing valve, and a general electro-hydraulic proportional reversing valve consists of a direct-acting proportional pressure reducing valve and a hydraulic reversing valve, wherein the proportional pressure reducing valve serves as a pilot stage, and the hydraulic reversing valve serves as a power stage of the hydraulic reversing valve. The electro-hydraulic proportional pressure reducing valve controls the size of the valve opening under the pushing of the proportional electromagnet, and the outlet pressure of the electro-hydraulic proportional pressure reducing valve is used as a control signal to drive the main valve element of the hydraulic reversing valve to move, namely the input current of the proportional electromagnet is proportional to the size of the pilot valve opening, the size of the pilot valve opening is proportional to the control pressure, namely the electromagnetic force is proportional to the control pressure, and the control pressure is proportional to the displacement of the main valve element, so that the direction and the flow of liquid flow can be controlled by changing the control current input into the electromagnet.
The general electro-hydraulic proportional reversing valve has a direct-acting proportional pressure reducing valve as a pilot stage, so the volume is large, the manufacturing cost is high, the response speed of the electro-hydraulic proportional reversing valve is reduced due to the existence of the proportional pressure reducing valve, the pilot-operated proportional reversing valve cannot work under zero pilot control pressure, and although the direct-acting proportional reversing valve can work under the zero pressure condition, the direct-acting proportional reversing valve cannot adapt to a large-flow occasion due to the limitation of the stroke of a proportional electromagnet, so the structure of the pilot control stage needs to be innovated. On the basis, the Yuan Jian and the like of Zhejiang industrial university provide an electro-hydraulic proportional reversing valve based on two degrees of freedom (2D) of a valve core, a guide control stage and a power stage are combined into a whole, the 2D valve and a proportional electromagnet are combined together through a compression-torsion coupler, the size of the valve body is reduced, the structure is compact, and the pollution resistance is strong. Under the condition of zero pressure, the valve can work according to the principle of a direct-acting type proportional reversing valve, has the advantages of the direct-acting type and pilot type electro-hydraulic proportional reversing valves, and has good dynamic response characteristics. The main problems of the valve are that two proportion electromagnets and two compression-torsion couplers are adopted, so that the axial size of the valve body is very large, the requirement on installation space is high, and the structure is relatively complex. Most of the conventional half bridge couplings use a ball screw assembly or an elastic spring assembly. The ball screw type coupling needs to accurately control the size of a helix angle, otherwise, the phenomenon of locking can occur, the screw is seriously abraded, the service life of parts is shortened, and the maintenance cost is increased; the elastic reed coupling can greatly affect the response characteristic of the electro-hydraulic proportional reversing valve due to the existence of the elastic element, and the service life of parts can be affected due to the action of bending moment in the working process of the reed, so that the reed coupling needs to be replaced regularly.
Disclosure of Invention
In order to overcome the problems, the invention provides a two-dimensional half-bridge electro-hydraulic proportional reversing valve based on a push rod central roller coupling.
The technical scheme adopted by the invention is as follows: the two-dimensional half-bridge electro-hydraulic proportional reversing valve based on the push rod middle-mounted roller coupling comprises a bidirectional proportional electromagnet (1), the push rod middle-mounted roller coupling and a 2D half-bridge electro-hydraulic proportional reversing valve body which are sequentially arranged from left to right, wherein the 2D half-bridge electro-hydraulic proportional reversing valve body comprises a valve body (7), a valve sleeve (8) and a valve core (9), the bidirectional proportional electromagnet (1) is installed at the left end of the valve body (7), the push rod middle-mounted roller coupling is installed at the left end of the valve core (9), and the valve core (9) is connected with the bidirectional proportional electromagnet (1) through the push rod middle-mounted roller coupling;
the push rod middle-mounted roller coupling comprises a left oblique wing rotor (4), a left pushing body (15), an inner oblique wing rotor (17), a right pushing body (18) and a right oblique wing rotor (5) which are sequentially arranged from left to right, wherein the left pushing body (15) is directly contacted with the left oblique wing rotor (4), the left end of the left pushing body (15) is provided with a horizontal leftward extension rod, and the extension rod penetrates through a central hole of the left oblique wing rotor (4), a left spring (12), a supporting end cover (3) and a proportional electromagnet base (2) and then is in threaded connection with a bidirectional proportional electromagnet (1) so as to avoid the axial displacement of the bidirectional proportional electromagnet (1) relative to the left pushing body (15) in the pushing and pulling process; the right pushing body (18) is directly contacted with the right oblique wing rotor (5), and the left end of the valve core (9) penetrates through the plug-in end cover (6), the right spring (20), the central hole of the right oblique wing rotor (5) and the right pushing body (18) leftwards and is connected with the inner oblique wing rotor (17); the left pushing body (15) and the right pushing body (18) are connected into a whole through a screw; the upper end and the lower end of the left oblique wing rotor (4) and the upper end and the lower end of the right oblique wing rotor (5) are respectively provided with a linear bearing (16), and the linear bearings (16) are sleeved on linear bearing guide rails (19) and are arranged between the supporting end cover (3) and the inserting end cover (6), so that the left oblique wing rotor (4) keeps horizontal linear motion under the pushing action of the pushing body; wing surfaces on two sides of the left oblique wing rotor (4), the right oblique wing rotor (5) and the inner oblique wing rotor (17) have a certain inclination angle beta and are all characterized in a 180-degree array by taking an axis vertical to a horizontal plane as a central axis; the upper surface and the lower surface of each side wing surface of the inner oblique wing rotor (17) are respectively provided with a roller support (13), a roller (14) is arranged in a groove of each roller support (13), the axis of each roller (14) is parallel to the corresponding wing surface, and the axial displacement of each roller (14) is limited by a roller clamp spring (22); when the inner oblique wing rotor (17) is in a neutral position state, the rollers (14) are tightly attached to the wing surfaces on two sides of the left oblique wing rotor (4) and the right oblique wing rotor (5) under the action of the left spring (12) and the right spring (20); the inner oblique wing rotor (17) is rotatably arranged between the left oblique wing rotor (4) and the right oblique wing rotor (5);
the valve core (9) is rotatably and axially movably arranged in an inner hole of the valve sleeve (8), a T port, an A port, a P port, a B port and a T port are sequentially arranged on the inner hole of the valve body (7), the two T ports are communicated through an overflowing channel on the valve body (7), the P port is an oil inlet, the pressure is system pressure, 5 steps are arranged on the valve core (9), a high-pressure oil area is formed between the two steps in the middle of the valve core (9), and oil is supplied to the system from the A port or the B port along with the movement of the valve core (9); the middle part and the left end of the valve core (9) are respectively provided with a first high-pressure hole (a) and a second high-pressure hole (b) which are respectively communicated with the P port and the left sensitive cavity (g) so that the left sensitive cavity (g) is constantly communicated with high pressure, the right end step of the valve core (9) is respectively provided with a third high-pressure hole (c) communicated with the P port and a low-pressure groove (f) communicated with the T port, the inner surface of the right end of the valve sleeve (8) is provided with a pair of axisymmetric straight groove sensing channels (e), one end of each straight groove sensing channel (e) is communicated with the right sensitive cavity (h), the other end of each straight groove sensing channel (e) forms hydraulic resistance with the third high-pressure hole (c) and the low-pressure groove (f), and the half-bridge resistance senses the pressure of oil in the right sensitive cavity (h) through the straight groove sensing channels (e).
Furthermore, the bidirectional proportional electromagnet (1) is fixedly connected with the proportional electromagnet base (2) through a screw, and the right end of the proportional electromagnet base (2) is fixedly connected with the supporting end cover (3); the right end of the supporting end cover (3) is fixedly connected with the plug-in end cover (6), and the right end of the plug-in end cover (6) is screwed with the valve sleeve (8) in a threaded manner; the plug-in end cover (6) is connected with the valve body (7) through screws, and the valve core (9) and the inner oblique wing rotor (17) are fixed at opposite positions through two fastening screws.
Furthermore, a plug (10) is arranged on the right side of an inner hole of the valve sleeve (8), and the plug (10) is fixed in the valve sleeve (8) through a fixing pin (11) so as to prevent oil from leaking from the right side of the 2D valve; the valve core (9) is sleeved with a concentric ring (21) to ensure the positioning of the valve core (9) in the inner hole of the valve sleeve (8).
Furthermore, the upper surface and the lower surface of each side wing surface of the inner oblique wing rotor are in a clamp shape, the roller support (13) is positioned through the clamp-shaped surface of the inner oblique wing rotor and is connected to the inner oblique wing rotor (17) through screws.
The invention has the beneficial effects that:
1. the two-dimensional half-bridge electro-hydraulic proportional reversing valve designed by the invention only needs a novel push rod middle-positioned roller coupling and a bidirectional proportional electromagnet, reduces the installation space by about 30 percent, has low requirement on the installation space, reduces the axial size of the electro-hydraulic proportional valve, and has simpler structure and convenient maintenance.
2. The two-dimensional half-bridge type electro-hydraulic proportional reversing valve designed by the invention adopts a novel coupling with a roller arranged in a push rod, solves the problem that the traditional ball screw type half-bridge type coupling is blocked due to improper selection of a thread lead angle, and solves the problem that the response speed of an elastic reed coupling is low due to the existence of an elastic element. The push rod central roller coupling is one mechanical coupling, and has high response speed, reduced friction, less wear of parts and long service life.
3. According to the two-dimensional half-bridge electro-hydraulic proportional reversing valve designed by the invention, the pushing body is arranged between the left inclined wing rotor and the right inclined wing rotor, so that the push rod middle-mounted roller coupling can realize bidirectional pressure torsion, and can realize the function of bidirectional proportional control by being matched with a bidirectional linear electro-mechanical converter for use.
4. Compared with the traditional pilot type electro-hydraulic control element, the action of the main valve core of the power stage of the traditional pilot type proportional valve depends on stable pilot pressure, so that the traditional pilot type electro-hydraulic proportional reversing valve cannot normally work under the zero-pressure condition, and the two-dimensional electro-hydraulic proportional reversing valve can work according to the working principle of a direct-acting proportional valve under the zero-pressure condition; the valve can work according to the working principle of the pilot-controlled proportional valve under the condition of normal working pressure, and the direct-acting-pilot-controlled integrated design is successfully realized.
5. The two-dimensional half-bridge electro-hydraulic proportional reversing valve designed by the invention adopts a two-dimensional hydraulic amplifying mechanism with two degrees of freedom of the valve core, the rotation of the valve core is taken as a pilot stage, the axial movement of the valve core is taken as a power stage, and the pilot stage and the power stage are integrated on a single valve core, so that the two-dimensional half-bridge electro-hydraulic proportional reversing valve has the advantages of simple structure, low processing cost and greatly improved power-weight ratio.
Drawings
FIG. 1 is an assembly schematic diagram of a two-dimensional half-bridge electro-hydraulic proportional reversing valve based on a push rod central roller coupling;
FIG. 2 is an exploded view of the new coupling with rollers in the middle of the push rod;
fig. 3 is a schematic structural diagram of the left oblique wing rotor 4;
fig. 4 is a schematic structural diagram of a right oblique wing rotor 5;
fig. 5 is a schematic structural diagram of an inner oblique wing rotor 17;
FIG. 6 is a schematic view of the roller support 13;
fig. 7 is a schematic view of the left half of the pushing assembly-the left pusher body 15;
FIG. 8 is a schematic structural view of the right half of the pushing assembly, the right pusher 18;
FIG. 9 is a schematic view of the assembly of the new push rod roller coupling with the valve core 9;
FIG. 10 is a schematic structural diagram of a proportional electromagnet base 2;
fig. 11 is a schematic structural view of the support end cap 3;
FIG. 12 is a schematic structural view of the cartridge end cap 6;
FIG. 13 is a schematic view of the thrust rod center-positioned roller coupling in a neutral position under stress;
fig. 14a to 14c are schematic diagrams of the working principle of the two-dimensional half-bridge electro-hydraulic proportional directional valve, wherein fig. 14a is a schematic diagram of a neutral balance state of the two-dimensional half-bridge electro-hydraulic proportional directional valve, fig. 14b is a schematic diagram of a valve core of the two-dimensional half-bridge electro-hydraulic proportional directional valve after the proportional electromagnet is electrified, and fig. 14c is a schematic diagram of the valve core of the two-dimensional half-bridge electro-hydraulic proportional directional valve moving axially and reaching a new balance state.
Description of reference numerals: 1. a bidirectional proportional electromagnet; 2. a proportional electromagnet base; 3. supporting the end cap; 4. a left oblique wing rotor; 5. a right oblique wing rotor; 6. inserting an end cover; 7 a valve body; 8. a valve housing; 9. a valve core; 10. a plug; 11. a fixing pin; 12. a left spring; 13. supporting a roller; 14. a roller; 15. a left pusher; 16. a linear bearing; 17. an inner oblique wing rotor; 18. a right pusher; 19. a linear bearing guide rail; 20. a right spring; 21. concentric rings; 22. a roller clamp spring;
Detailed Description
The technical solutions of the present invention will be described clearly and completely with reference to the accompanying drawings, and it should be understood that the described embodiments are only some embodiments, but not all embodiments, of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the present invention, it should be noted that the orientations or positional relationships indicated as the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., appear based on the orientations or positional relationships shown in the drawings only for the convenience of describing the present invention and simplifying the description, but not for indicating or implying that the referred devices or elements must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" as appearing herein are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless otherwise explicitly stated or limited, the terms "mounted," "connected," and "connected" should be interpreted broadly, e.g., as being fixed or detachable or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Referring to the attached drawings, the two-dimensional half-bridge electro-hydraulic proportional reversing valve based on the push rod middle-mounted roller coupling comprises a bidirectional proportional electromagnet 1, the push rod middle-mounted roller coupling and a 2D half-bridge electro-hydraulic proportional reversing valve body which are sequentially arranged from left to right, wherein the 2D half-bridge electro-hydraulic proportional reversing valve body comprises a valve body 7, a valve sleeve 8 and a valve core 9, the bidirectional proportional electromagnet 1 is installed at the left end of the valve body 7, the push rod middle-mounted roller coupling is installed at the left end of the valve core 9, and the valve core 9 is connected with the bidirectional proportional electromagnet 1 through the push rod middle-mounted roller coupling;
the push rod middle-mounted roller coupling comprises a left oblique wing rotor 4, a left pushing body 15, an inner oblique wing rotor 17, a right pushing body 18 and a right oblique wing rotor 5 which are sequentially arranged from left to right, wherein the left pushing body 15 is directly contacted with the left oblique wing rotor 4, the left end of the left pushing body 15 is provided with a horizontal leftward extension rod, and the extension rod penetrates through a central hole of the left oblique wing rotor 4, a left spring 12, a supporting end cover 3 and a proportional electromagnet base 2 and then is in threaded connection with a bidirectional proportional electromagnet 1, so that the bidirectional proportional electromagnet 1 is prevented from generating relative axial displacement with the left pushing body 15 in the pushing and pulling process; the right pushing body 18 is directly contacted with the right oblique wing rotor 5, and the left end of the valve core 9 penetrates through the plug-in end cover 6, the right spring 20, the central hole of the right oblique wing rotor 5 and the right pushing body 18 leftwards and then is connected with the inner oblique wing rotor 17; the left pushing body 15 and the right pushing body 18 are connected into a whole through a screw; the upper end and the lower end of the left oblique wing rotor 4 and the right oblique wing rotor 5 are respectively provided with a linear bearing 16, and the linear bearings 16 are sleeved on a linear bearing guide rail 19 and are arranged between the supporting end cover 3 and the inserting end cover 6, so that the left oblique wing rotor 4 keeps horizontal linear motion under the pushing action of the pushing body; the wing surfaces on the two sides of the left oblique wing rotor 4, the right oblique wing rotor 5 and the inner oblique wing rotor 17 have a certain inclination angle beta and are all characterized in a 180-degree array by taking an axis vertical to the horizontal plane as a central axis; the upper surface and the lower surface of each side wing surface of the inner oblique wing rotor 17 are respectively provided with a roller support 13, a roller 14 is arranged in a groove of the roller support 13, the axis of the roller 14 is parallel to the corresponding wing surface, and the axial displacement of the roller 14 is limited by a roller clamp spring 22; when the inner oblique wing rotor 17 is in a neutral state, the rollers 14 are tightly attached to the two side wing surfaces of the left oblique wing rotor 4 and the right oblique wing rotor 5 under the action of the left spring 12 and the right spring 20; the inner oblique wing rotor 17 is rotatably arranged between the left oblique wing rotor 4 and the right oblique wing rotor 5;
the body of the 2D half-bridge type electro-hydraulic proportional directional valve comprises a valve body 7, a valve sleeve 8, a valve core 9, concentric rings 21, a plug 10 and a fixing pin 11, wherein the valve core 9 is rotatably and axially movably arranged in an inner hole of the valve sleeve 8, the plug 10 is arranged on the right side of the inner hole of the valve sleeve 8, and the plug 10 is fixed in the valve sleeve 8 through the fixing pin 11 so as to prevent oil from leaking from the right side of the 2D valve; concentric rings 21 are provided around the valve spool 9 to ensure the positioning of the valve spool 9 within the bore of the valve housing 8. The bidirectional proportional electromagnet 1 is fixed on a proportional electromagnet base 2 through screws, the proportional electromagnet base 2 is connected with a supporting end cover 3 through screws, the supporting end cover 3 is fixed on an insertion end cover 6 through screws, a valve sleeve 8 is screwed with the insertion end cover 6 through threads, the insertion end cover 6 is connected with a valve body 7 through screws, and a valve core 9 and an inner oblique wing rotor 17 of the 2D valve are fixed at relative positions through two fastening screws. An inner hole of the valve body 7 is sequentially provided with a T port, an A port, a P port, a B port and a T port, the two T ports are communicated through an overflowing channel on the valve body 7, the P port is an oil inlet, the pressure is system pressure, 5 steps are arranged on the valve core 9, a high-pressure oil area is formed between the two steps in the middle of the valve core 9, and oil is supplied to the system from the A port or the B port along with the movement of the valve core 9; the middle part and the left end of the valve core 9 are respectively provided with a first high pressure hole a and a second high pressure hole b which are respectively communicated with the port P and the left sensitive cavity g, so that the left sensitive cavity g is constantly communicated with high pressure, the right end step of the valve core 9 is respectively provided with a third high pressure hole c communicated with the port P and a low pressure groove f communicated with the port T, the inner surface of the right end of the valve sleeve 8 is provided with a pair of axisymmetric straight groove sensing channels e, one end of each straight groove sensing channel e is communicated with the right sensitive cavity h, the other end of each straight groove sensing channel e, the third high pressure hole c and the low pressure groove f form a hydraulic resistance half bridge, and the resistance half bridge controls the pressure of oil in the right sensitive cavity h through the straight groove sensing channels e. The left spring 12 and the right spring 20 are respectively arranged at two sides of the push rod middle-positioned roller coupling, mainly realize the conversion of the output force and the displacement of the bidirectional proportional electromagnet 1, and play a role in eliminating a gap and enabling the axial opening of a main valve to be in zero position alignment when the bidirectional proportional electromagnet 1 is not electrified.
The bidirectional proportional electromagnet 1 of the two-dimensional half-bridge electro-hydraulic proportional reversing valve is a commercial product mature in the market, and the central push rod type roller coupling is mainly used for converting axial displacement generated by the bidirectional proportional electromagnet 1 into rotary motion of a valve core.
The working principle of the implementation of the invention is shown in fig. 14 a-14 c. When the proportional electromagnet 1 of the two-dimensional electro-hydraulic proportional reversing valve is not electrified, as shown in fig. 14a, the pushing body (the combination of the left pushing body 15 and the right pushing body 18) is in the neutral position, and the spring force F generated by the left spring 12t1And the spring force F generated by the right spring 20t2The left oblique wing rotor 4 and the right oblique wing rotor 5 are tightly pressed on two sides of the pushing body, and the pushing body is at a stressed level at the momentAnd (5) balancing the state. The spring force is transmitted to the inner oblique wing rotor 17 through the left oblique wing rotor 4 and the right oblique wing rotor 5, and is decomposed into two forces F capable of driving the inner oblique wing rotor 17 and the valve core 9 to rotate1And F3Since the oblique wing surfaces of the inner oblique wing rotor 17, the oblique wing surfaces of the left oblique wing rotor 4 and the oblique wing surfaces of the right oblique wing rotor 5 are all arranged in a 180-degree array with the central axis as the center, the inner oblique wing rotor 17 is subjected to two couple moments with equal magnitude and opposite directions, and the inner oblique wing rotor 17 is also in a balanced state. When the bidirectional proportional electromagnet 1 of the two-dimensional electro-hydraulic proportional reversing valve outputs an F to the leftmWhen the left spring 12 is further compressed, as shown in fig. 14b, the constraint force F between the left oblique wing mover 4 and the inner oblique wing mover 17 is generated1Will disappear, since the left spring 12 and the right spring 20 are compressed in the initial neutral position, the right spring 20 will push the right oblique wing mover 5 to move to the left under the guiding action of the guide rail 19, because F1Disappears, so is divided by the spring force F3The formed moment of couple will drive the inner oblique wing mover 17 and the valve core 9 to rotate in the counterclockwise direction (from right to left) by Δ θ, and as the valve core 9 rotates, the flow areas of the straight slot sensing channel e on the inner surface of the rightmost end of the valve sleeve 8 and the high pressure hole c and the low pressure slot f on the rightmost step of the valve core 9 will change correspondingly, wherein the flow areas of the high pressure hole c and the straight slot sensing channel e increase, and the flow areas of the low pressure slot f and the straight slot sensing channel e decrease, so the oil pressure in the right sensitive cavity h will increase, and the oil pressure in the left sensitive cavity g will remain unchanged, and the valve core 9 will be pushed to move leftward by Δ x due to the effect of the pressure difference, as shown in fig. 14 c. With the left movement of the valve core 9, the rollers 14 on the inner oblique wing rotor 17 will again touch the oblique wing surface of the left oblique wing rotor 4, and then the inner oblique wing rotor 17 will again receive the constraint force F of the oblique wing surface of the left oblique wing rotor 41And rotate clockwise until F1Increase to again and F3When the two are equal, the inner oblique wing rotor 17 and the valve core 9 stop rotating and reach balance again at a new position, at the moment, the oil port A is an oil supply port, the oil port B is an oil return port, and the actuating mechanism is controlled to make corresponding action. When the two-dimensional electro-hydraulic proportional reversing valve is bidirectionalAfter the proportional electromagnet 1 receives the signal of returning to the neutral position, an electromagnetic thrust F with the same magnitude is output to the rightmThis electromagnetic thrust force FmWhen the pressure difference is formed by the change of the high-low pressure groove flow area, the valve core 9 is pushed to move to the right by delta x, the roller 14 contacts the right oblique wing mover 5 again and starts to rotate in the counterclockwise direction, and the valve core 9 stops rotating until the high-low pressure groove flow area is the same again, and the middle position state is returned. It should be noted that, under the working condition that the 2D electro-hydraulic proportional valve is at zero pressure, the valve plug 9 cannot be driven to axially move by using the pressure difference between the left sensitive chamber g and the right sensitive chamber h. At the moment, no oil liquid flows in the valve cavity, the valve core 9 is not influenced by hydrodynamic force and clamping force, the valve core 9 can be directly driven by electromagnetic thrust generated by the bidirectional proportional electromagnet 1, and at the moment, the working principle of the two-dimensional electro-hydraulic proportional reversing valve is consistent with that of a 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 (4)
1. Two-dimensional half-bridge electro-hydraulic proportional reversing valve based on push rod central roller coupling is characterized in that: the two-way proportional electromagnetic valve comprises a two-way proportional electromagnet (1), a push rod middle-mounted roller coupling and a 2D half-bridge type electro-hydraulic proportional reversing valve body which are sequentially arranged from left to right, wherein the 2D half-bridge type electro-hydraulic proportional reversing valve body comprises a valve body (7), a valve sleeve (8) and a valve core (9), the two-way proportional electromagnet (1) is installed at the left end of the valve body (7), the push rod middle-mounted roller coupling is installed at the left end of the valve core (9), and the valve core (9) is connected with the two-way proportional electromagnet (1) through the push rod middle-mounted roller coupling;
the push rod middle-mounted roller coupling comprises a left oblique wing rotor (4), a left pushing body (15), an inner oblique wing rotor (17), a right pushing body (18) and a right oblique wing rotor (5) which are sequentially arranged from left to right, wherein the left pushing body (15) is directly contacted with the left oblique wing rotor (4), the left end of the left pushing body (15) is provided with a horizontal leftward extension rod, and the extension rod penetrates through a central hole of the left oblique wing rotor (4), a left spring (12), a supporting end cover (3) and a proportional electromagnet base (2) and then is in threaded connection with a bidirectional proportional electromagnet (1) so as to avoid the axial displacement of the bidirectional proportional electromagnet (1) relative to the left pushing body (15) in the pushing and pulling process; the right pushing body (18) is directly contacted with the right oblique wing rotor (5), and the left end of the valve core (9) penetrates through the plug-in end cover (6), the right spring (20), the central hole of the right oblique wing rotor (5) and the right pushing body (18) leftwards and is connected with the inner oblique wing rotor (17); the left pushing body (15) and the right pushing body (18) are connected into a whole through a screw; the upper end and the lower end of the left oblique wing rotor (4) and the upper end and the lower end of the right oblique wing rotor (5) are respectively provided with a linear bearing (16), and the linear bearings (16) are sleeved on linear bearing guide rails (19) and are arranged between the supporting end cover (3) and the inserting end cover (6), so that the left oblique wing rotor (4) keeps horizontal linear motion under the pushing action of the pushing body; wing surfaces on two sides of the left oblique wing rotor (4), the right oblique wing rotor (5) and the inner oblique wing rotor (17) have a certain inclination angle beta and are all characterized in a 180-degree array by taking an axis vertical to a horizontal plane as a central axis; the upper surface and the lower surface of each side wing surface of the inner oblique wing rotor (17) are respectively provided with a roller support (13), a roller (14) is arranged in a groove of each roller support (13), the axis of each roller (14) is parallel to the corresponding wing surface, and the axial displacement of each roller (14) is limited by a roller clamp spring (22); when the inner oblique wing rotor (17) is in a neutral position state, the rollers (14) are tightly attached to the wing surfaces on two sides of the left oblique wing rotor (4) and the right oblique wing rotor (5) under the action of the left spring (12) and the right spring (20); the inner oblique wing rotor (17) is rotatably arranged between the left oblique wing rotor (4) and the right oblique wing rotor (5);
the valve core (9) is rotatably and axially movably arranged in an inner hole of the valve sleeve (8), a T port, an A port, a P port, a B port and a T port are sequentially arranged on the inner hole of the valve body (7), the two T ports are communicated through an overflowing channel on the valve body (7), the P port is an oil inlet, the pressure is system pressure, 5 steps are arranged on the valve core (9), a high-pressure oil area is formed between the two steps in the middle of the valve core (9), and oil is supplied to the system from the A port or the B port along with the movement of the valve core (9); the middle part and the left end of the valve core (9) are respectively provided with a first high-pressure hole (a) and a second high-pressure hole (b) which are respectively communicated with the P port and the left sensitive cavity (g) so that the left sensitive cavity (g) is constantly communicated with high pressure, the right end step of the valve core (9) is respectively provided with a third high-pressure hole (c) communicated with the P port and a low-pressure groove (f) communicated with the T port, the inner surface of the right end of the valve sleeve (8) is provided with a pair of axisymmetric straight groove sensing channels (e), one end of each straight groove sensing channel (e) is communicated with the right sensitive cavity (h), the other end of each straight groove sensing channel (e) forms hydraulic resistance with the third high-pressure hole (c) and the low-pressure groove (f), and the half-bridge resistance senses the pressure of oil in the right sensitive cavity (h) through the straight groove sensing channels (e).
2. The two-dimensional half-bridge electro-hydraulic proportional directional control valve based on the push rod central roller coupling as claimed in claim 1, wherein: the bidirectional proportional electromagnet (1) is fixedly connected with the proportional electromagnet base (2) through a screw, and the right end of the proportional electromagnet base (2) is fixedly connected with the supporting end cover (3); the right end of the supporting end cover (3) is fixedly connected with the plug-in end cover (6), and the right end of the plug-in end cover (6) is screwed with the valve sleeve (8) in a threaded manner; the plug-in end cover (6) is connected with the valve body (7) through screws, and the valve core (9) and the inner oblique wing rotor (17) are fixed at opposite positions through two fastening screws.
3. The two-dimensional half-bridge electro-hydraulic proportional directional control valve based on the push rod central roller coupling as claimed in claim 1, wherein: a plug (10) is arranged on the right side of an inner hole of the valve sleeve (8), and the plug (10) is fixed in the valve sleeve (8) through a fixing pin (11) so as to prevent oil from leaking from the right side of the 2D valve; the valve core (9) is sleeved with a concentric ring (21) to ensure the positioning of the valve core (9) in the inner hole of the valve sleeve (8).
4. The two-dimensional half-bridge electro-hydraulic proportional directional control valve based on the push rod central roller coupling as claimed in claim 1, wherein: the upper surface and the lower surface of each side wing surface of the inner oblique wing rotor are in a clamp shape, and the roller support (13) is positioned through the clamp-shaped surface of the inner oblique wing rotor and is connected to the inner oblique wing rotor (17) through screws.
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| CN113775586B (en) * | 2021-08-18 | 2024-07-19 | 浙江工业大学 | Two-dimensional full-bridge electro-hydraulic proportional reversing valve based on pincer displacement amplification coupling |
| CN115095572B (en) * | 2022-07-21 | 2024-05-28 | 湖南十开科技有限公司 | Double-acting electro-hydraulic proportional push rod and electro-hydraulic proportional multi-way valve |
| CN115750902B (en) * | 2022-11-29 | 2023-06-09 | 富阳通力机械制造有限公司 | Two-dimensional electro-hydraulic proportional valve manual unloading structure for quick self-locking jack |
| CN118337138B (en) * | 2024-06-13 | 2024-08-23 | 国网安徽省电力有限公司宿州供电公司 | Photovoltaic board that zero carbon transformer substation used |
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Application publication date: 20210618 Assignee: LISHUI ZHENGXIANG PEN INDUSTRY Co.,Ltd. Assignor: JIANG University OF TECHNOLOGY Contract record no.: X2023980037309 Denomination of invention: A two-dimensional half bridge electro-hydraulic proportional directional valve based on a push rod central roller coupling Granted publication date: 20220318 License type: Common License Record date: 20230630 |
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Application publication date: 20210618 Assignee: ZHEJIANG HUANYI ELECTRONIC TECHNOLOGY CO.,LTD. Assignor: JIANG University OF TECHNOLOGY Contract record no.: X2023980037571 Denomination of invention: A two-dimensional half bridge electro-hydraulic proportional directional valve based on a push rod central roller coupling Granted publication date: 20220318 License type: Common License Record date: 20230706 |