Electromagnetic hydraulic valve

Abstract

This invention discloses an electromagnetic hydraulic valve, comprising a valve structure and an electromagnetic control structure fixed to each other. The valve structure includes a valve body, a valve cover, a valve stem, and a valve core. The electromagnetic control structure includes a magnetic shell, a first stationary iron core, a second stationary iron core, an armature, and a push rod. The opening sides of the first and second stationary iron cores are both wedge-shaped, and their cross-sections form a V-shaped gap structure. When the coil is de-energized, the armature and push rod are in a first position, with the distal end face of the armature in the direction of movement flush with the end face of the first wedge-shaped side. The wedge-shaped end face structure and angle setting of the first and second stationary iron cores, along with the initial position of the armature when the electromagnetic control structure is de-energized, help optimize the electromagnetic field distribution after the electromagnetic control structure is energized, limit the direction of magnetic lines of force, ensure that the initial electromagnetic force on the armature is sufficiently large, and that the electromagnetic force remains almost constant during the movement of the armature.

Description

Technical Field

[0001] This invention relates to the field of solenoid valve technology, and more particularly to an electromagnetic hydraulic valve. Background Technology

[0002] Hydraulic valves are core control components in hydraulic systems, primarily controlling the flow direction, pressure, and flow rate of hydraulic oil (the working medium). Electromagnetic hydraulic valves are a special type of hydraulic valve that uses an electromagnet to generate driving force. When the electromagnet is energized or de-energized, it generates attraction, directly pushing the valve core to move, thereby changing the flow direction of the hydraulic oil or opening / closing the hydraulic oil passage. Because the electromagnet operates rapidly, it is suitable for applications requiring frequent reversals, and therefore, the application of electromagnetic hydraulic valves is becoming increasingly widespread.

[0003] Chinese patent CN 104265978 B discloses a dual-purpose electromagnetic hydraulic valve, including a valve body, a valve core, a valve stem, and a connecting seat. An electromagnetic control structure is provided above the connecting seat. The electromagnetic control structure includes a stationary iron core, an electromagnet sleeved on the outside of the stationary iron core, and a threaded centering sleeve located on the upper part of the stationary iron core and connected to the stationary iron core by a threaded sleeve. There is a cavity between the threaded centering sleeve and the stationary iron core. A moving iron core is provided in the cavity. An L-shaped lever is provided in the connecting seat. The outer end of the valve stem abuts against one end of the L-shaped lever, and the lower end of the moving iron core abuts against the other end of the L-shaped lever. Although this hydraulic valve achieves the blocking / opening of the hydraulic oil flow channel, because the stationary iron core and the threaded centering sleeve are set in a planar opposite position, a large part of the magnetic lines of force will be transmitted between the stationary iron core and the threaded centering sleeve after the electromagnet coil is energized. This results in insufficient electromagnetic force on the moving iron core. Furthermore, the change in the air gap between the moving iron core and the stationary iron core during the movement causes the electromagnetic force to change too much, which in turn affects the moving speed of the moving iron core. The relatively large speed difference will affect the control effect of the solenoid valve.

[0004] US Patent 7367355B2 discloses another type of electromagnetic hydraulic valve. The valve body structure also includes a valve core, valve stem, and connecting seat. The electromagnetic control structure that plays a control role includes a housing, a stationary iron core fixed on the housing, an electromagnet coil located in sequence inside the housing, and an armature. When the electromagnet coil is energized, it magnetizes the housing and the armature to generate electromagnetic force, thereby driving the armature to move. Because the contact area between the armature and the housing is small and continues to decrease during the movement of the armature, premature magnetic saturation will occur between the housing and the armature, which will also lead to insufficient electromagnetic force on the armature and excessive variation. Summary of the Invention

[0005] The purpose of this invention is to overcome the shortcomings of the existing technology and provide an electromagnetic hydraulic valve in which the initial electromagnetic force on the armature of its electromagnetic control structure is large enough and the electromagnetic force remains almost constant during the movement of the armature.

[0006] The objective of this invention is achieved through the following technical solution: An electromagnetic hydraulic valve includes a valve structure and an electromagnetic control structure fixed to each other. The valve structure includes a valve body, a valve cover, a valve stem, and a valve core. The valve body and valve cover are fixed to each other and both have a common internal opening to form a flow channel. The valve stem receives power generated by the electromagnetic control structure to drive the valve core to move from a first position blocking the flow channel to a second position opening the flow channel. The electromagnetic control structure includes a magnetic shell, a coil located inside the magnetic shell, a first stationary iron core and a second stationary iron core respectively fixed at both ends of the magnetic shell and disposed inside the coil, and the electromagnetic control structure also includes an armature and a push rod fixed to each other. Both the iron core and the second stationary iron core are frame structures and are arranged opposite to each other. The armature is located in the receiving space enclosed by the first stationary iron core and the second stationary iron core. The two ends of the push rod pass through the first stationary iron core and the second stationary iron core respectively. The opening side of the first stationary iron core is the first wedge side, and the opening side of the second stationary iron core is the second wedge side. The end faces of the first wedge side and the second wedge side are arranged opposite to each other at intervals. The cross-sections of the first wedge side and the second wedge side have a V-shaped gap structure. When the coil is de-energized, the armature and the push rod are in the first position, and the far end face of the armature in the direction of movement is flush with the end face of the first wedge side.

[0007] Preferably, the angle between the cross-sectional line of the first wedge side (2041) and the axis of the push rod (207) is set to between 35° and 40°; the angle between the cross-sectional line of the second wedge side and the axis of the push rod is set to between 20° and 40°.

[0008] Preferably, the first stationary iron core and the second stationary iron core are fixed by welding with a sleeve, the sleeve being made of 304 stainless steel and fitted over the outside of the first stationary iron core and the second stationary iron core.

[0009] Preferably, it also includes a magnetic shielding pad, which is fixedly sleeved on the push rod and disposed between the armature and the second stationary iron core.

[0010] Preferably, a resilient button is fixed to the top of the second stationary iron core, and the first end of the push rod extends into its internal space.

[0011] Preferably, a spring is provided between the armature and the first stationary iron core; both the first and second stationary iron cores are provided with sliding guide sleeves that are slidably connected to the push rod.

[0012] Preferably, a plug assembly is fixed to the outside of the magnetic shell, and the plug assembly is locked to the magnetic shell by a locking bolt; the plug of the plug assembly is electrically connected to the coil; the coil is wound on a coil frame, and the coil frame is fixed inside the magnetic shell.

[0013] Preferably, the valve structure further includes a hydraulic oil inlet and a hydraulic oil outlet located on the valve body, both of which are connected to the flow channel; The valve structure also includes a connecting seat for fixing the valve body and the electromagnetic control structure. An L-shaped lever is provided inside the connecting seat via a pivot pin. The connecting seat is fixed to the flange structure of the first stationary iron core. The second end of the push rod extends into the connecting seat and abuts against the free end of the L-shaped lever. The middle driving section of the L-shaped lever always abuts against the first end of the valve stem. The second end of the valve stem always abuts against the valve core. The valve core is a spherical seal.

[0014] Preferably, the valve structure further includes a front valve seat and a rear valve seat fixed to both sides of the valve body, both of which are fixed to the valve body by an interference flange structure; both the front valve seat and the rear valve seat are provided with through holes for the valve stem to pass through, and the portions of both extending into the valve body are sealed with sealing rings between them and the hollow channel of the valve body.

[0015] Preferably, the valve structure further includes a return spring and a sealing block disposed within the valve cover. The return spring always exerts a thrust on the sealing block to press the valve core tightly. When the valve stem does not exert a driving force on the valve core, the sealing block receives the spring force of the return spring to press the valve core tightly against the sealing surface of the front valve seat.

[0016] The beneficial effects of this invention are mainly reflected in: The wedge-shaped end face structure and angle setting of the first and second stationary iron cores, along with the structure in which the armature and push rod are in the first position and the far end face of the armature's movement direction is flush with the end face of the first wedge-shaped side when the coil is de-energized, help to optimize the electromagnetic field distribution after the electromagnetic control structure is energized, limit the direction of the magnetic field lines, make the initial electromagnetic force on the armature sufficiently large, and ensure that the electromagnetic force remains almost constant during the movement of the armature.

[0017] The sleeve made of 304 stainless steel is welded to the outside of the first and second stationary iron cores, which can effectively ensure the sealing of the receiving space enclosed by the first and second stationary iron cores and prevent external impurities from entering and affecting the performance of the solenoid valve. At the same time, the austenitic crystal structure of the sleeve can reduce magnetic field leakage and further improve the working efficiency and performance stability of the solenoid valve.

[0018] The front and rear valve seats, located on both sides of the valve body, are fixed to the valve body by an interference flange structure, which reduces the risk of sliding of the front and rear valve seats and ensures that the valve stem effectively holds the valve core to complete the seal. Attached Figure Description

[0019] The technical solution of the present invention will be further described below with reference to the accompanying drawings: Figure 1 : A perspective view of a preferred embodiment of the electromagnetic hydraulic valve of the present invention; Figure 2 : Front view of a preferred embodiment of the electromagnetic hydraulic valve of the present invention; Figure 3 : Figure 2 A cross-sectional view along HH, at which point the coil of the electromagnetic control structure is de-energized; Figure 4 : Figure 3 A magnified view of part A in the middle; Figure 5 : Figure 3 A magnified view of part C in the middle; Figure 6 : A cross-sectional view of a preferred embodiment of the electromagnetic hydraulic valve of the present invention, in which the coil of the electromagnetic control structure is energized; Figure 7 : Figure 6 A magnified view of part B in the middle section; Figure 8 : A schematic diagram of the magnetic circuit simulation of the electromagnetic hydraulic valve of this invention; Figure 9 : A magnetic simulation diagram of the electromagnetic hydraulic valve with a second static iron core wedge angle of 20° according to the present invention; Figure 10 : A magnetic simulation diagram of the electromagnetic hydraulic valve with a second static iron core wedge angle of 40° according to the present invention. Detailed Implementation

[0020] The present invention will now be described in detail with reference to the specific embodiments shown in the accompanying drawings. However, these embodiments are not limited to the present invention, and any structural, methodological, or functional modifications made by those skilled in the art based on these embodiments are included within the scope of protection of the present invention.

[0021] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicating orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined with "first," "second," etc., may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0022] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art will understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0023] The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0024] like Figure 1 , Figure 2 , Figure 3 As shown, the present invention discloses an electromagnetic hydraulic valve, which, like the prior art, includes a valve structure 1 and an electromagnetic control structure 2 that are fixed to each other.

[0025] The valve structure 1 includes a valve body 101, a valve cover 103, a valve stem 104, and a valve core 105. The valve body 101 and the valve cover 103 are fixed to each other, and a flow channel 102 is formed inside both of them. The valve body 101 is provided with a hydraulic oil inlet 108 and a hydraulic oil outlet 109, both of which are connected to the flow channel 102. In this embodiment, the positions of the hydraulic oil inlet 108 and the hydraulic oil outlet 109 are merely examples, and are well known to those skilled in the art; other positions are also feasible.

[0026] The valve structure 1 also includes a connecting seat 106 for fixing the valve structure 1 and the electromagnetic control structure 2. Similar to existing technologies, the connecting seat 106 is fixed to the flange structure of the first stationary iron core 204. Its structure is a hollow frame structure, with an L-shaped lever 107 pivotally mounted inside via a pin 115. The control method of the L-shaped lever 107 will be detailed later.

[0027] The valve structure 1 further includes a front valve seat 110 and a rear valve seat 111 respectively fixed to both sides of the valve body 101. Both are fixed to the valve body 101 by an interference-fit flange structure. Both the front valve seat 110 and the rear valve seat 111 have through holes for the valve stem 104 to pass through, and the portions of both extending into the valve body 101 are sealed with a sealing ring 114 between themselves and the hollow channel of the valve body 101. The interference-fit flange structure reduces the risk of sliding of the front and rear valve seats, and the sealing ring ensures that the valve stem 104 effectively presses against the valve core 105 to complete the seal. Preferably, the valve core 105 is a spherical sealing element.

[0028] The valve structure 1 also includes a return spring 112 and a sealing block 113 disposed within the valve cover 103. The return spring 112 always exerts a pushing force on the sealing block 113 to press the valve core 105 against it. When the valve stem 104 does not exert a driving force on the valve core 105, the sealing block 113 receives the spring force of the return spring 112 to press the valve core 105 against the sealing surface of the front valve seat 110. When the valve stem 104 receives the power generated by the electromagnetic control structure 2, it drives the valve core 105 to move from a first position blocking the flow channel 102 to a second position opening the flow channel 102. The valve structure 1 also includes conventional technical structures such as a pressure relief port and a filter screen, which will not be described in detail in this embodiment.

[0029] The improvement of this invention lies in the electromagnetic control structure 2. As shown in the figure, the electromagnetic control structure 2 includes a cylindrical magnetic shell 201, a coil 202 located inside the magnetic shell 201, the coil 202 being wound on a coil frame 203, and the coil frame 203 being fixed inside the magnetic shell 201. In this embodiment, a stop block, similar to those in the prior art, is used to fix the coil frame 203 inside the magnetic shell 201.

[0030] A plug assembly 212 is fixed to the outer side of the magnetic housing 201. The plug assembly 212 is locked to the magnetic housing 201 by a locking bolt 214. The plug assembly 212 has an arc-shaped connecting part that matches the outer contour of the magnetic housing 201, ensuring that the plug assembly 212 can be firmly installed on the magnetic housing 201, preventing the plug from loosening and causing electrical connection failure, and improving the reliability of the solenoid valve. The plug of the plug assembly 212 is electrically connected to the coil 202. Specifically, the connecting side of the plug is a pin, which can be easily mated with the mating end of the coil 202 to realize the transmission of electrical control signals, enabling the solenoid valve to work accurately according to external commands.

[0031] The magnetic shell 201 has a first stationary iron core 204 and a second stationary iron core 205 fixed at both ends. The first stationary iron core 204 and the second stationary iron core 205 are welded together by a sleeve 211, which is made of 304 stainless steel and is fitted over the outside of the first stationary iron core 204 and the second stationary iron core 205. After the three are integrated, they are inserted into the magnetic shell 201, located inside the coil 202, and are limited by the flange structure of the first stationary iron core 204.

[0032] The electromagnetic control structure also includes an armature 206 and a push rod 207 fixed to each other. The first stationary iron core 204 and the second stationary iron core 205 are both frame structures and are arranged opposite each other. The armature 206 is located within the receiving space enclosed by the first stationary iron core 204 and the second stationary iron core 205. The two ends of the push rod 207 pass through the first stationary iron core 204 and the second stationary iron core 205 respectively. A resilient button 208 for manual operation is fixed to the top of the second stationary iron core 205. The first end of the push rod 207 extends into its internal space. The second end of the push rod 207 extends into the connecting seat 106 and abuts against the free end of the L-shaped lever 107. The middle driving section of the L-shaped lever 107 always abuts against the first end of the valve stem 104, and the second end of the valve stem 104 always abuts against the valve core 105.

[0033] A spring 209 is provided between the armature 206 and the first stationary iron core 204; both the first stationary iron core 204 and the second stationary iron core 205 are provided with sliding guide sleeves 210 that are slidably connected to the push rod 207, providing good support and guidance for the sliding of the push rod 207 and preventing the push rod from getting stuck. In this preferred embodiment, a magnetic shielding pad 213 is also included, which is fixedly sleeved on the push rod 207 and disposed between the armature 206 and the second stationary iron core 205.

[0034] Combination Figure 3 , Figure 4 , Figure 6 , Figure 7 Here is a brief explanation of the working process of this invention: like Figure 3 , Figure 4 In the initial state shown, the coil 202 is de-energized, and the electromagnetic control structure 2 does not generate electromagnetic force. At this time, the spring 209 is in its natural state, that is, the armature 206, the push rod 207, and the L-shaped lever 107 are all in their initial positions. The first end of the valve stem 104 is not under force, while the valve core 105 is pressed against the front valve seat 110 by the return spring 112 and the sealing block 113 to form a seal, blocking the flow channel 102.

[0035] When the coil 202 is energized, the electromagnetic control structure 2 generates electromagnetic force, driving the armature 206 and push rod 207 to move simultaneously toward the first stationary iron core 204. During the movement, the armature 206 compresses the spring 209, while the push rod 207 pushes the free end of the L-shaped lever 107. The L-shaped lever 107 rotates around the pin 115, and its middle driving section pushes the first end of the valve stem 104, causing the valve stem 104 to move. Its second end pushes the valve core 105 away from the front valve seat 110, creating a gap 1021 between them. This opens the flow channel 102 until the flow reaches the desired destination. Figure 6 , Figure 7 The second position shown in the figure indicates the direction of hydraulic oil flow, as indicated by the arrow.

[0036] Combination Figure 2 and Figure 3 As shown, the present invention adjusts the structure of the first stationary iron core 204 and the second stationary iron core 205. The opening side of the first stationary iron core 204 is the first wedge-shaped side 2041, and the opening side of the second stationary iron core 205 is the second wedge-shaped side 2051. The end faces 2042 of the first wedge-shaped side 2041 and 2051 are spaced apart from each other, and the cross-sections of the first wedge-shaped side 2041 and the second wedge-shaped side 2051 have a V-shaped gap structure. When the coil 202 is de-energized, the armature 206 and the push rod 207 are in the first position, and the distal end face 2061 of the armature 206 in the direction of movement is flush with the end face 2042 of the first wedge-shaped side 2041. The axial movement distance between the distal end face 2061 of the armature 206 in the direction of movement and the first stationary iron core 204 is g (longitudinal), and the distance between the armature 206 and the second stationary iron core 205 is g (lateral).

[0037] When the electromagnetic control structure 2 is energized for a moment, combined with Figure 8The schematic diagram of the magnetic circuit shows that the coil 202 begins to magnetize the magnetic shell 201, the first stationary iron core 204, and the second stationary iron core 205. Magnetic lines of force then form a loop between the magnetic shell 201, the second stationary iron core 205, the armature 206, and the second stationary iron core 205. Furthermore, since the length of the sleeve (i.e., the part used to house the armature) of the second stationary iron core 205 is approximately equal to that of the armature 206, and the cross-sections of the first wedge-shaped side 2041 and the second wedge-shaped side 2051 have a V-shaped gap structure, most of the magnetic lines of force will be transmitted from the second stationary iron core 205 to the armature 206. And since the distal end face 2061 of the armature 206 in the direction of movement is flush with the end face 2042 of the first wedge-shaped side 2041, most of the magnetic lines of force will also be transmitted from the armature 206 to the first stationary iron core 204. Therefore, at the instant the electromagnetic control structure 2 is energized, the magnetic flux on the armature 206 is much larger than in the prior art, and only a small portion of the magnetic field lines will be transmitted from the second stationary iron core 205 to the first stationary iron core 204. This effectively limits the electromagnetic field distribution after the direction of the magnetic field lines, making the initial electromagnetic force on the armature sufficiently large. The direct effect of this is a faster response speed of the electromagnetic hydraulic valve. Because the initial electromagnetic force on the armature is large, the acceleration of the armature 206 and the push rod 207 is several times greater than in the prior art. Furthermore, during the movement of the armature 206 and the push rod 207, the total contact area between the armature 206 and the first stationary iron core 204 and the second stationary iron core 205 remains almost constant. This also means that the magnetic flux passing through the three can remain roughly constant, thus keeping the electromagnetic force almost constant during the movement of the armature, and the acceleration of the armature 206 and the push rod 207 also almost constant.

[0038] Preferably, in this invention, the angle between the cross-sectional line of the first wedge-shaped side 2041 and the axis of the push rod 207 is set between 35° and 40°; the angle between the cross-sectional line of the second wedge-shaped side 2051 and the axis of the push rod 207 is set between 20° and 40°. This is a preferred range obtained based on actual measurement data. A simple calculation is presented below using an example.

[0039] The standard expression for the electromagnetic force acting on the armature is:

[0040] in: F: Electromagnetic force, measured in Newtons (N); N: Number of coil turns (fixed); I: Current through the coil, measured in amperes (A); μ0: Vacuum permeability, a constant; A: Effective cross-sectional area of ​​the magnetic circuit, in square meters (m²). g: The length of the air gap between the armature and the core, in meters (m).

[0041] Theoretically, the smaller the gap g, the stronger the electromagnetic force. The gap g consists of two parts: g lateral and g longitudinal. The longitudinal force directly affects the direction of motion, while the lateral force, through force decomposition, can partially affect the direction of motion.

[0042] g lateral: The lateral force (g) affects the generated lateral force. The frictional force generated by the direct contact between the armature and the stationary iron core is relatively large (the direct friction coefficient between low-carbon steels is approximately 0.1-0.2), and the frictional resistance affects the force in the direction of motion. Therefore, the gap between the armature and the stationary iron core is set to a tolerance of 0.225-0.315mm, with the lower limit being twice the maximum gap between the friction surfaces and the upper limit considering manufacturing level. Simultaneously, as mentioned above, to maximize the initial electromagnetic force, the distal end face of the armature is flush with the end face of the first wedge-shaped side, ensuring that the lateral air gap remains within its minimum range.

[0043] g longitudinal direction: Theoretically, the smaller the longitudinal g, the greater the downward force, assuming other parameters are the same. However, this gap directly affects the movement distance; the smaller the gap, the smaller the movement distance. Therefore, considering the movement of the hydraulic valve, for the armature to move downwards by 5mm, the hydraulic valve shaft needs to be able to push the valve core to move by at least 1mm, a ratio of approximately 1:5. Since the movement distance of the steel ball is generally required to be 0.5mm, the longitudinal g is set to 2.5mm.

[0044] The calculated value is artan(2 / 2.5) = 38.66°. When the angle is less than 38.66°, the electromagnetic force will weaken. Considering the machining process, the angle between the cross-sectional line of the first wedge side 2041 and the axis of the push rod 207 is set to an integer of 40°.

[0045] To maximize the electromagnetic force, an extension line is drawn along the hypotenuse of the second stationary iron core to the bottom of the armature. The electromagnetic force of the armature is maximized when the magnetic field can propagate along this path. Simultaneously, the two stationary iron cores must not be in contact (similar to existing technology), otherwise the magnetic field will preferentially propagate along a closed loop. In this example, considering processing factors, the median distance between the two stationary iron cores is 1.2 mm. Considering the air gap and the width of the pole sleeve end, the optimal angle can be calculated as artan(0.45 / 1.2) = 20.56°. When the distance 1.2 takes other values, the angle can be changed. Therefore, the angle between the cross-sectional line of the second wedge side 2051 and the axis of the push rod 207 should preferably be between 20° and 40°.

[0046] Inputting the above parameters into the MAXWELL simulation, the number of turns was set to 2772, and the current was kept constant at 1.1A. The wedge angle of the second stationary core was set to 20° and 40°. It can be seen that the initial electromagnetic force at 0 stroke is about 4N, the overall electromagnetic force is slightly larger at 0-1mm (0-2N), and slightly smaller at 0-3N in the latter half. This meets the requirement that a larger electromagnetic force is needed for startup, and the electromagnetic force requirement decreases slightly after subsequent opening.

[0047] It should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This way of describing the specification is only for clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0048] The detailed descriptions listed above are merely specific descriptions of feasible embodiments of the present invention, and are not intended to limit the scope of protection of the present invention. All equivalent embodiments or modifications made without departing from the spirit of the present invention should be included within the scope of protection of the present invention.

Claims

1. An electromagnetic hydraulic valve, comprising a valve structure (1) and an electromagnetic control structure (2) fixed to each other, wherein the valve structure (1) comprises a valve body (101), a valve cover (103), a valve stem (104), and a valve core (105), wherein the valve body (101) and the valve cover (103) are fixed to each other and both have a flow channel (102) formed inside them, wherein the valve stem (104) receives power generated by the electromagnetic control structure (2) to drive the valve core (105) to move from a first position blocking the flow channel (102) to a second position opening the flow channel (102); wherein the electromagnetic control structure comprises a magnetic shell (201) located inside the magnetic shell (201). The coil (202) is fixed at both ends of the magnetic shell (201) and disposed inside the coil (202) by a first stationary iron core (204) and a second stationary iron core (205). The electromagnetic control structure also includes an armature (206) and a push rod (207) fixed to each other. The first stationary iron core (204) and the second stationary iron core (205) are both frame structures and are disposed opposite to each other. The armature (206) is located in the receiving space enclosed by the first stationary iron core (204) and the second stationary iron core (205). The two ends of the push rod (207) pass through the first stationary iron core (204) and the second stationary iron core (205) respectively. The characteristic of the structure is that: The opening side of the first stationary iron core (204) is the first wedge-shaped side (2041), and the opening side of the second stationary iron core (205) is the second wedge-shaped side (2051). The end face (2042) of the first wedge-shaped side (2041) and the end face (2052) of the second wedge-shaped side (2051) are arranged at intervals. The cross-section of the first wedge-shaped side (2041) and the second wedge-shaped side (2051) has a V-shaped gap structure. When the coil (202) is de-energized, the armature (206) and the push rod (207) are in the first position. The far end face (2061) of the armature (206) in the direction of movement is flush with the end face (2042) of the first wedge-shaped side (2041).

2. The electromagnetic hydraulic valve according to claim 1, characterized in that: The angle between the cross-sectional line of the first wedge side (2041) and the axis of the push rod (207) is set to between 35° and 40°; the angle between the cross-sectional line of the second wedge side (2051) and the axis of the push rod (207) is set to between 20° and 40°.

3. The electromagnetic hydraulic valve according to claim 1, characterized in that: The first stationary iron core (204) and the second stationary iron core (205) are fixed by welding through a sleeve (211). The sleeve (211) is made of 304 stainless steel and is fitted on the outside of the first stationary iron core (204) and the second stationary iron core (205).

4. The electromagnetic hydraulic valve according to claim 1, characterized in that: It also includes a magnetic shielding pad (213), which is fixedly sleeved on the push rod (207) and positioned between the armature (206) and the second stationary iron core (205).

5. The electromagnetic hydraulic valve according to claim 1, characterized in that: A resilient button (208) is fixed to the top of the second static iron core (205), and the first end of the push rod (207) extends into its internal space.

6. The electromagnetic hydraulic valve according to claim 1, characterized in that: A spring (209) is provided between the armature (206) and the first stationary iron core (204); both the first stationary iron core (204) and the second stationary iron core (205) are provided with sliding guide sleeves (210) that are slidably connected to the push rod (207).

7. The electromagnetic hydraulic valve according to claim 1, characterized in that: A plug assembly (212) is fixed to the outside of the magnetic shell (201), and the plug assembly (212) is locked to the magnetic shell (201) by a locking bolt (214); the plug of the plug assembly (212) is electrically connected to the coil (202); the coil (202) is wound on the coil frame (203), and the coil frame (203) is fixed inside the magnetic shell (201).

8. The electromagnetic hydraulic valve according to any one of claims 1 to 7, characterized in that: The valve structure (1) further includes a hydraulic oil inlet (108) and a hydraulic oil outlet (109) located on the valve body (101), and the hydraulic oil inlet (108) and the hydraulic oil outlet (109) are both connected to the flow channel (102); The valve structure (1) further includes a connecting seat (106) for fixing the valve body (101) and the electromagnetic control structure (2). An L-shaped lever (107) is pivotally provided inside the connecting seat (106) via a pin (115). The connecting seat (106) is fixed to the flange structure of the first stationary iron core (204). The second end of the push rod (207) extends into the connecting seat (106) and abuts against the free end of the L-shaped lever (107). The middle driving section of the L-shaped lever (107) always abuts against the first end of the valve stem (104). The second end of the valve stem (104) always abuts against the valve core (105). The valve core (105) is a spherical seal.

9. The electromagnetic hydraulic valve according to claim 8, characterized in that: The valve structure (1) further includes a front valve seat (110) and a rear valve seat (111) respectively fixed on both sides of the valve body (101), both of which are fixed to the valve body (101) by an interference flange structure; the front valve seat (110) and the rear valve seat (111) are both provided with through holes for the valve stem (104) to pass through, and the portions of both extending into the valve body (101) are sealed with a sealing ring (114) between them and the hollow channel of the valve body (101).

10. The electromagnetic hydraulic valve according to claim 9, characterized in that: The valve structure (1) also includes a return spring (112) and a sealing block (113) disposed in the valve cover (103). The return spring (112) always exerts a thrust on the sealing block (113) to press the valve core (105) tightly. When the valve stem (104) does not exert a driving force on the valve core (105), the sealing block (113) receives the spring force of the return spring (112) to press the valve core (105) tightly on the sealing surface of the front valve seat (110).

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