Design method of valve core fast response electromagnetic valve, spring series large flow normally open electromagnetic valve and pressure regulation method thereof

Abstract

The application provides a design method of a valve core fast-response electromagnetic valve, a spring series large-flow constant-opening electromagnetic valve and a pressure regulation method thereof. The electromagnetic valve comprises an electromagnetic coil, a valve shell, a moving iron, a valve core, a small-flow valve seat, a large-flow valve seat, a first spring and a second spring. The inside of the valve shell is sequentially provided with the valve core, the small-flow valve seat and the large-flow valve seat from top to bottom. The upper end of the valve core is connected with the moving iron, and the electromagnetic coil is arranged around the moving iron and the valve shell. The first spring and the second spring are connected in series. The first spring and the second spring are connected with the small-flow valve seat and act on the upper and lower ends of the small-flow valve seat. The technical scheme can realize greater reset force of the small-flow valve seat, so that the small-flow valve seat is opened faster when the electromagnetic valve is powered off, that is, the large-flow response speed of the electromagnetic valve is faster.

Description

TECHNICAL FIELD

[0001] The application relates to the technical field of electromagnetic valves, in particular to a design method of a valve core fast-response electromagnetic valve, a spring series large-flow normally-open electromagnetic valve and a pressure regulation method thereof. BACKGROUND

[0002] In the application 202411225759.X "normally-open large-flow switching electromagnetic valve and hydraulic control unit of automobile brake system", a large-flow normally-open electromagnetic valve is provided, which mainly functions as follows: 1) when the electromagnetic coil is not powered, the valve core and the small-flow valve seat are kept open under the action of the spring force, at this time, the liquid in the upper inlet and the lower inlet can flow through the small-flow port and the large-flow port to the outlet, that is, the normally-open large-flow function of the electromagnetic valve; 2) when the electromagnetic coil is powered, the fixed iron is attracted to the moving iron under the action of the magnetic field, pushing the valve core to close the small-flow port, at this time, the high-pressure fluid entering the upper end of the small-flow valve seat through the upper inlet will accumulate, increasing the pressure at the upper end of the small-flow valve seat, which will move downward under the action of the pressure and close the large-flow port, since the small-flow port area is smaller than the large-flow port area, the two-stage closing mode of first closing the small-flow port and then closing the large-flow port under the action of the pressure difference can reduce the electromagnetic force required for closing the electromagnetic valve, that is, the current of the electromagnetic coil can be reduced; 3) when the electromagnetic valve switches from the powered state to the unpowered state, there is no electromagnetic force between the moving iron and the fixed iron, the valve core is reset under the action of the spring, opening the small-flow port, at this time, the high-pressure fluid at the upper end of the small-flow port will flow to the outlet through the small-flow port, the pressure at this position will decrease, and when the downward force at this position is less than the sum of the upward force of the high-pressure fluid in the lower inlet and the reset force of the second spring, the small-flow valve seat moves upward and the large-flow port opens, which is a two-stage reset process. Through the above design, the normally-open large-flow valve realizes the functions of normally-open, two-stage closing and two-stage reset, so that the on-off of the large-flow hydraulic circuit can be controlled by a smaller electromagnetic force. However, the prior art still has the following problems: it relies too much on the downward force generated by the pressure difference between the upper and lower ends of the small-flow valve seat, which increases the design difficulty of the electromagnetic valve and slows down the response speed of the small-flow valve seat when the electromagnetic valve is unpowered; there is a stepped contact area between the small-flow valve seat and the valve shell, which mainly functions to limit the highest position of the small-flow valve seat and form a sealing area to divide the small-flow valve seat into two independent areas, but this area cannot be filled with liquid, resulting in that the fluid acting area above the small-flow valve seat is much smaller than that below the small-flow valve seat, so that the small-flow valve seat needs a larger pressure above to close, making it more difficult to close. SUMMARY

[0003] Therefore, the present application aims to provide a design method of a valve core quick-response electromagnetic valve, a spring series large-flow normally open electromagnetic valve and a pressure control method thereof, so as to realize greater reset force of a small-flow valve seat, and make the small-flow valve seat open faster when the electromagnetic valve is powered off, that is, the large-flow response speed of the electromagnetic valve is faster.

[0004] To achieve the above-mentioned purpose, the present application adopts the following technical solutions: a design method of a valve core quick-response electromagnetic valve, the electromagnetic valve comprising an electromagnetic coil, a valve shell, a moving iron, a valve core, a small-flow valve seat, a large-flow valve seat, a first spring and a second spring; the inside of the valve shell is sequentially provided from top to bottom with the valve core, the small-flow valve seat and the large-flow valve seat, the upper end of the valve core is connected with the moving iron, and the electromagnetic coil is arranged around the moving iron and the valve shell; the first spring and the second spring are connected in series, and both the first spring and the second spring are connected with the small-flow valve seat and act on the upper and lower ends of the small-flow valve seat.

[0005] The design method comprises the following steps:

[0006] Step A1: calculating variable data, the variables including valve inlet pressure P1, valve outlet pressure P2, inlet equivalent area A1, small-flow valve seat throttling port area A2, small-flow valve seat upper acting area A3, small-flow valve seat lower acting area A4, area A5 surrounded by the tangent line of the contact between the small-flow valve seat and the large-flow valve seat, force F s1 of the first spring when the valve is closed, and force F s2 of the second spring when the valve is closed;

[0007] Step A2: according to the throttling formula when the single cavity input and output are both throttled, when the electromagnetic valve is powered off, the valve core is opened, at this time, the pressure P x of the space above the small-flow valve seat is calculated as , at this time, the pressure of the space above the small-flow valve seat acts on the valve core, the force of the small-flow valve seat downward is , the lower part of the small-flow valve seat is directly connected with the inlet, and the large valve port is in a closed state at this time, at this time, the acting area of the valve inlet pressure P1 is (A4-A5), the pressure of the lower part acts on the valve core, and the force of the small-flow valve seat upward is , if the small-flow valve seat is not opened at the same time when the valve core is opened, all the forces acting on the large-flow valve seat downward should be greater than the forces upward, that is, , then ; when the valve core is opened, P2 gradually increases, and P1 gradually decreases, when to , the small-flow valve core moves upward, at this time, the large-flow port of the electromagnetic valve is opened.

[0008] The application also provides a spring series large flow normally open electromagnetic valve based on the design method of the valve core fast response electromagnetic valve, the upper and lower ends of the small flow valve seat are respectively an upper cylindrical protrusion and a lower cylindrical protrusion, the upper cylindrical protrusion is connected with the first spring, and the lower cylindrical protrusion is connected with the second spring.

[0009] The upper end of the small flow valve seat is provided with a circle of side edge guides in the circumferential direction or the side edge of the small flow valve seat is provided with a side edge guide, the inner side of the side edge guide forms a circle of grooves for accommodating the first spring.

[0010] In a preferred embodiment, the part of the valve shell facing the small flow valve seat is provided with a first liquid guide groove, and the first liquid guide groove is uniformly provided with a plurality of first liquid guide grooves in the circumferential direction of the valve shell.

[0011] In a preferred embodiment, the part of the small flow valve seat facing the valve shell is provided with a plurality of second liquid guide grooves, and the second liquid guide grooves are uniformly provided with a plurality of second liquid guide grooves in the circumferential direction of the small flow valve seat.

[0012] The application also provides a pressure control method based on the spring series large flow normally open electromagnetic valve, which comprises the following steps.

[0013] Step B1: obtaining the PV characteristic curve of the controlled cavity, denoted as ; wherein P is the pressure difference between the valve inlet and the valve outlet, V ch (P) represents the curve of the volume, i.e. the conversion relationship between pressure P and volume;

[0014] Step B2: according to the PV characteristic curve, calculating the initial volume V a and the target volume V b ;

[0015] Step B3: calculating the flow volume required for one-time opening of the large valve port;

[0016] Step B4: calculating the flow volume left for the large valve port in the flow stable stage, comparing the required volume with the minimum flow volume;

[0017] Step B5: proposing a pressure control logic.

[0018] In a preferred embodiment, the step B1 specifically comprises:

[0019] Step B11: measuring the pressure difference P between the valve inlet and the valve outlet and the flow Q, controlling in the order of power-on-power-off-power-on, measuring the correlation of the flow with respect to time, repeating the above process under different pressure differences P to obtain a group of flow-time curves related to the pressure P; integrating the flow with respect to time before reaching the large flow stable stage to obtain the flow volume function of the valve opening The time taken for this process is recorded as Integrating the flow rate over time from energization to zero yields the flow volume function when the valve is closed. The time taken for this process is recorded as The flow rate during the steady-state phase when the valve is fully open is denoted as . ;

[0020] Step B12: Under different pressures, starting from 1ms, increase the power-off interval by 1ms each time to control the valve core to open until the valve seat at low flow rate shows a tendency to open. Integrate the flow rate over time to obtain the flow volume function with power-off time t under pressure difference P. The function of determining the required power outage time t based on the required flow volume is denoted as: .

[0021] In a preferred embodiment, step B3 specifically includes: calculating the flow volume required to open the large valve port in one operation. ,in, The pressure to be controlled until the end of control, i.e., the target pressure P. b Total required flow volume The small valve port is at the target pressure P b The flow volume within the next control cycle T, with K being a correction factor ≥ 2, ensures that at least two adjustment cycles are allowed for subsequent small valve ports, P b The target pressure is the pressure at the end of the control process.

[0022] In a preferred embodiment, step B4 specifically includes: reserving a flow volume for the large valve orifice during the flow stabilization phase. , where V l P represents the flow volume required to open the valve once through the large valve port. a To control the initial pressure, P b To control the final pressure, i.e. the target pressure, V O (P a V represents the flow volume function of the valve opening at the start of control. O (P b This represents the flow volume function of the valve opening at the end of the control phase, and calculates the average of the opening and closing phases. Q avg (P a ) indicates that P a Substitute The obtained flow, Q avg (P b ) indicates that P b Substitute The obtained traffic; then the duration of the traffic stabilization phase is: The total time for the large valve to open once should be wherein, T O (P a ) represents the time that the control start process experiences, T O (P b ) represents the time that the control end process experiences, and the minimum volume of flow is If the required volume is less than the minimum volume of flow, then the large valve port does not need to be opened to ensure response speed, and the determination condition is recorded as .

[0023] In a preferred embodiment, the step B5 specifically comprises:

[0024] Step B51: When the outlet pressure P2 has not reached the target pressure P b , that is, : first determine whether is satisfied, if not, the large valve port needs to be opened, at this time the control electromagnetic valve de-energization time , in this stage, de-energization is maintained and no operation is performed, and then energization is performed; if satisfied, directly jump to step B52;

[0025] Step B52: When the outlet pressure P2 has not reached the target pressure P b , that is, : cycle control is performed according to the period T, and the electromagnetic valve de-energization time in each period is , if t s > T, the electromagnetic valve is directly fully de-energized in this period; wherein V ch (P b ) and V ch (P2) are respectively calculated based on V ch (P).

[0026] Step B53: Repeat B52 until is not satisfied.

[0027] Compared with the prior art, the present application has the following beneficial effects: 1) When the liquid flow channel is designed, the requirement value of the downward force generated by the pressure difference between the upper and lower ends of the small flow valve seat is lower, that is, the design difficulty is lower; 2) A greater reset force of the small flow valve seat 4 can be designed, so that the small flow valve seat opens faster when the electromagnetic valve is de-energized, that is, the large flow response speed of the electromagnetic valve is faster; 3) The change of the design value of the first spring only affects the opening and closing of the valve core, and does not affect the external force of the small flow valve seat under the action of the electromagnetic force, which makes it possible to arbitrarily adjust the design value (including the pre-pressure and the spring stiffness) of the first spring to adjust the response characteristics of the valve core, for example, the opening speed when de-energized can be increased by increasing the pre-pressure or stiffness of the first spring, or the closing speed when energized can be increased by reducing the pre-pressure or stiffness of the first spring. BRIEF DESCRIPTION OF DRAWINGS

[0028] Figure 1 A cross-sectional view of an electromagnetic valve according to a preferred embodiment of the present application;

[0029] Figure 2 A schematic view of a second side edge guide position relationship according to a preferred embodiment of the present application;

[0030] Figure 3 A schematic view of a first liquid guide groove relationship according to a preferred embodiment of the present application;

[0031] Figure 4 A schematic view of a first liquid guide groove in a small flow valve seat and valve shell limiting overlap area according to a preferred embodiment of the present application;

[0032] Figure 5 A schematic view of a second liquid guide groove relationship according to a preferred embodiment of the present application;

[0033] Figure 6 A schematic view of a second liquid guide groove in a small flow valve seat and valve shell limiting overlap area according to a preferred embodiment of the present application;

[0034] Figure 7 A schematic view of variable positions in step Al according to a preferred embodiment of the present application;

[0035] Figure 8 A power-on time flow curve according to a preferred embodiment of the present application;

[0036] Figure 9 A pressure (P) - volume (V) curve according to a preferred embodiment of the present application. DETAILED DESCRIPTION

[0037] The present application will be further described with reference to the drawings and embodiments.

[0038] It should be noted that the following detailed description is exemplary in nature and is intended to provide further description of the application. Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs.

[0039] It is also important to note that the terms "including", "comprising", and / or "having" as used herein are specifically intended to be open-ended and also to mean including, but not limited to. As used herein, the singular forms "a", "an" and / or "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. Further, it will be understood that the terms "comprises", "comprising", "includes" and / or "including", when used herein, specify the presence of stated features, steps, operations, elements, components and / or combinations thereof, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components and / or combinations thereof.

[0040] Reference Figures 1-9, the valve core 3 fast response solenoid valve design method, the solenoid valve includes electromagnetic coil, valve shell 1, moving iron 2, valve core 3, small flow valve seat 4, large flow valve seat 5, first spring 6 and second spring 7;The inside of the valve shell 1 is sequentially provided with the valve core 3, the small flow valve seat 4 and the large flow valve seat 5 from top to bottom, the upper end of the valve core 3 is connected with the moving iron 2 and the electromagnetic coil is arranged around the moving iron 2 and the valve shell 1;The position relationship of the electromagnetic coil, valve shell 1, moving iron 2, valve core 3, small flow valve seat 4 and large flow valve seat 5 of the solenoid valve is consistent with the solenoid valve structure disclosed in patent application CN119196102A, which is different from the present application, in which the first spring 6 and the second spring 7 are connected in series, the first spring 6 and the second spring 7 are connected with the small flow valve seat 4 and act on the upper and lower ends of the small flow valve seat 4;The upper and lower ends of the small flow valve seat 4 are respectively upper and lower cylindrical protrusions, the upper cylindrical protrusion is connected with the first spring 6, and the lower cylindrical protrusion is connected with the second spring 7, which can prevent the spring from shaking and tilting;The main advantage of spring connection is that the electromagnetic force acting on the valve core 3 will be transmitted to the small flow valve seat 4 through the first spring 6, at this time the force that makes the small flow valve seat 4 close is the downward electromagnetic force + the downward force generated by the pressure difference between the upper and lower ends of the small flow valve seat 4, which only needs to be greater than the restoring force of the second spring 7 to make the small flow valve seat 4 close, compared with the downward force generated by the pressure difference between the upper and lower ends of the small flow valve seat 4 in the prior art, the force in the present application is larger, which means that it is easier to make the small flow valve seat 4 close.

[0041] As shown in Figure 1 , in order to ensure that the up and down movement of the small flow valve seat 4 in the valve shell 1 does not shake, the first side edge 41 of the small flow valve seat 4 is used as the guide of the valve shell 1.

[0042] In addition to Figure 1 the side edge guide, an upper side edge guide design form as shown in Figure 2 is also proposed, the upper end of the small flow valve seat 4 is provided with a circle of second side edge guide 42 in the circumferential direction, the inner side of the second side edge guide 42 forms a circle of grooves for accommodating the first spring 6, so that the side edge of the groove serves as the guide of the valve shell 1. By arranging the first spring 6 in the upper groove of the small flow valve seat 4, the side edge of the upper groove can also be used as the guide of the valve shell 1. This way reduces the risk that the side edge guide shown in Figure 1 may be scraped by the lower inlet, and reduces the design difficulty.

[0043] In order to solve the problem of unstable closure of the small flow valve seat 4, a design as shown in Figures 3-4As shown, the part of the valve housing 1 facing the small flow valve seat 4 is provided with a first liquid guide groove 11, which is uniformly provided with multiple along the circumference of the valve housing 1, so that the liquid below the small flow valve seat 4 can act on the small flow valve seat 4 through the first liquid guide groove 11, so that the equivalent acting area of the fluid on the lower surface of the small flow valve seat 4 is reduced (the pressure at the first liquid guide groove 11 of the upper and lower surfaces is equal, the force generated by the pressure is offset, which directly leads to the reduction of the acting area), reducing the pressure required for the small flow valve seat 4 to close. This measure realizes the reduction of pressure requirement while retaining the limiting function, and still has a certain overlapping area to ensure sealing.

[0044] Based on this idea, as shown, Figures 5-6 , an outer groove can also be opened on the small flow valve seat 4, that is, the part of the small flow valve seat 4 facing the valve housing 1 is provided with multiple second liquid guide grooves 43, which are uniformly provided with multiple along the circumference of the small flow valve seat 4, achieving the same effect. The Figure 3 or Figure 5 structure shown can be freely selected according to the manufacturing process requirements.

[0045] The design method of the valve core 3 quickly responding to the electromagnetic valve includes the following steps:

[0046] Step A1: Calculate the variable data, including the valve inlet pressure P1, the valve outlet pressure P2, the inlet equivalent area A1, the small flow valve seat 4 throttling area A2, the small flow valve seat 4 upper acting area A3, the small flow valve seat 4 lower acting area A4, the area A5 surrounded by the tangent line of the small flow valve seat 4 and the large flow valve seat 5, the force F s1 of the first spring 6 when the valve is closed, and the force F s2 of the second spring 7 when the valve is closed;

[0047] Step A2: According to the throttling formula when the single cavity input and output are throttled, when the electromagnetic valve is de-energized, the valve core 3 is opened, at this time the pressure P x of the space above the small flow valve seat 4 is calculated as , at this time the pressure of the small flow valve seat 4 above the valve core 3, the force of the small flow valve seat 4 downward is , the lower part of the small flow valve seat 4 is directly connected with the inlet due to the closed large valve port at this time, the lower pressure is P1, the acting area of the lower pressure is (A4-A5), then the pressure of the lower part acting on the valve core 3, the force of the small flow valve seat 4 upward is , if the small flow valve seat 4 does not open at the same time when the valve core 3 opens, then all the forces acting on the large flow valve seat 5 downward should be greater than the upward force, that is, , then This formula is the design verification formula for opening valve core 3 first, followed by opening the small-flow valve core 3. Based on this formula, when valve core 3 opens, P2 will gradually increase, and P1 will gradually decrease. If the condition is not met, the low-flow valve core 3 will move upward, at which point the high-flow port of the solenoid valve will open. Based on According to the formula, the design of a solenoid valve that satisfies this characteristic should be: increase A1, decrease A2, increase A5, decrease A4, and increase F. s1 (Preload or spring stiffness), reduce F s2 (Pre-pressure or spring stiffness) By selecting one or more of these measures in combination, a solenoid valve that meets the fast response characteristics of valve core 3 can be designed.

[0048] Before using pressure regulation methods, the following preparations need to be made:

[0049] (1) Measure the pressure difference P and flow rate Q at the inlet and outlet of the valve, according to Figure 8 The solenoid valve control curve (energized-de-energized) shown is used for control, and the measured values ​​are as follows: Figure 8 The flow-time curves shown can be repeated under different pressure differentials P to obtain a set of flow-time curves related to pressure P. Integrating the flow rate before reaching a stable high flow rate over time yields the flow volume function of the valve opening. The time taken for this process can also be recorded as Integrating the flow rate over time from energization to zero yields the flow volume function at valve closure. The time taken for this process can also be recorded as The flow rate during the steady-state phase when the valve is fully open (excluding the opening and closing phases) can be denoted as: .

[0050] (2) Under different pressures, starting from 1ms, the power-off interval is increased by 1ms each time to open the control valve core 3 until the small flow valve seat 4 shows a tendency to open. The flow volume function with time integration can be obtained for the power-off time t under the pressure difference P. The function of the required power outage time t, derived from the required flow volume Vs, is denoted as: .

[0051] (3) The PV characteristic curve of the controlled cavity is measured and denoted as . .

[0052] Pressure regulation methods include the following steps:

[0053] Step 1: For ease of description, let P be the initial pressure at the start of control. a The pressure at which control ends (target pressure) is P. b The current export pressure is P2;

[0054] Step 2: Calculate the initial volume V a , and the target volume V b according to the PV characteristic curve.

[0055] Step 3: Calculate the flow volume needed for the large valve to open once as V , where V is the total flow volume needed to control to P b , V is the flow volume of the small valve at the target pressure P b in one control period T, K is a correction factor >=2 to ensure at least 2 adjustment periods left for the subsequent small valve, and P b is the target pressure.

[0056] Step 4: Calculate the flow volume left for the large valve in the flow stabilization stage as V , where V l is the flow volume needed for the large valve to open once, P a is the pressure at the beginning of control, P b is the target pressure, V O (P a ) is the flow volume function of valve opening at the beginning of control, and V O (P b ) is the flow volume function of valve opening at the end of control. Since the pressure is continuously changing during the flow stage, the flow rate during this stage is simply calculated as the average of the beginning and end stages, i.e. , and the time needed for the flow stabilization stage is , then the total time for the large valve to open once should be , where T O (P a ) is the time experienced during the beginning of control, and T O (P b ) is the time experienced during the end of control. In the above calculation, t s is 0 when the minimum time for the large valve to open and close is reached, and the minimum flow volume during this time is V . If the required volume is less than this minimum flow volume, then the large valve does not need to open to ensure response speed, and the decision condition is .

[0057] Step B5: Pressure control logic

[0058] Step B51: When the outlet pressure P2 has not reached the target pressure P b , i.e. : First determine If not, the large valve port needs to be opened, and the solenoid valve is de-energized at this time In this stage, the de-energization is maintained and no operation is performed, and then energization is performed; if yes, it is directly jumped to step B52;

[0059] Step B52: the outlet pressure P2 has not reached the target pressure P b , that is : the cycle control is performed in a period T, and the de-energization time of the solenoid valve in each period is , if s t

[0060] Step B53: B52 is repeated until is not satisfied.

Claims

1. A design method of a spool quick response electromagnetic valve, the electromagnetic valve comprising an electromagnetic coil, a valve shell, a moving iron, a spool, a small flow valve seat, a large flow valve seat, a first spring, and a second spring; an inside of the valve shell is sequentially provided from top to bottom with the spool, the small flow valve seat, and the large flow valve seat, an upper end of the spool is connected with the moving iron, and the electromagnetic coil is arranged around the moving iron and the valve shell; characterized in that, The first spring and the second spring are connected in series, and the first spring and the second spring are connected with the small flow valve seat and act on the upper and lower ends of the small flow valve seat. The design method comprises the following steps: Step Al: Calculate variable data, variables include valve inlet pressure Pl, valve outlet pressure P2, inlet equivalent area Al, small flow valve seat orifice area A2, small flow valve seat upper acting area A3, small flow valve seat lower acting area A4, area A5 enclosed by the tangent line of small flow valve seat and large flow valve seat, force F of the first spring when the valve is closed s1 and force F of the second spring when the valve is closed s2 ; Step A2: according to the throttling formula when the single cavity input and output have throttling, then when the solenoid valve is powered off, the valve core is opened, at this time the pressure P of the space on the upper part of the small flow valve seat x The calculation is At this time, the pressure on the upper part of the small flow valve seat acts on the valve core, and the force of the small flow valve seat downward is The lower part of the small flow valve seat is directly connected to the inlet, and the large valve port is in a closed state at this time, so the acting area of the valve inlet pressure P1 is (A4-A5), and the force of the small flow valve seat upward is If the small flow valve seat is not opened at the same time when the valve core is opened, then the total force acting on the large flow valve seat downward should be greater than the upward force, that is, Then When the valve core is opened, P2 gradually increases and P1 gradually decreases, and when is not satisfied, the small flow valve core will move upward, and at this time the large flow port of the solenoid valve is opened.

2. A large flow on-off electromagnetic valve in series with a spring, characterized by The design method of the quick-response electromagnetic valve of the valve core according to claim 1, wherein the upper and lower ends of the small flow valve seat are respectively an upper cylindrical protrusion and a lower cylindrical protrusion, the upper cylindrical protrusion is connected with the first spring, and the lower cylindrical protrusion is connected with the second spring. The upper end of the small flow valve seat is provided with a circumferential side edge guide, or the side edge of the small flow valve seat is provided with a side edge guide, the inner side of the side edge guide forms a groove for accommodating the first spring.

3. The spring-loaded, in-line, high flow, normally open solenoid valve of claim 2, wherein, The inner side of the valve shell facing the small flow valve seat is provided with a first liquid guide groove, and the first liquid guide groove is uniformly provided with a plurality of first liquid guide grooves along the circumference of the valve shell.

4. The spring-loaded, in-line, high flow, normally open solenoid valve of claim 2, wherein, The part of the small flow valve seat facing the valve shell is provided with a plurality of second liquid guide grooves, and the second liquid guide grooves are uniformly provided with a plurality of second liquid guide grooves along the circumference of the small flow valve seat.

5. A method of pressure regulation, characterized by The spring series large flow normally open electromagnetic valve according to any one of claims 2-4 comprises the following steps: Step B1 : Obtain the PV characteristic curve of the controlled cavity, denoted as ; where P is the measured pressure difference between the valve inlet and the valve outlet end, V is the volume of the controlled cavity, and t is the time. ch (P) represents the volume curve, i.e. the conversion relationship of pressure P to volume. Step B2: Calculate the starting volume V a , and the target volume V b , according to the PV characteristic curve. Step B3: calculate the flow volume required for the large valve port to be opened once; Step B4: calculate the flow volume left for the large valve port in the flow stabilization stage, and compare the required volume with the minimum volume of the flow volume; Step B5: propose a pressure control logic.

6. The pressure regulation method of claim 5, wherein, The step B1 specifically comprises: Step B11: Measure the pressure difference P between the valve inlet and the valve outlet, and the flow rate Q, control in the sequence of power on-power off-power on, measure the correlation of flow rate and time, repeat the above process at different pressure difference P, get a group of flow rate-time curves related to pressure P; integrate the flow rate before reaching the stable stage of large flow rate to get the flow-through volume function of valve opening , the time taken by the process is recorded as ; integrate the flow rate from power on to the flow rate completely to 0 to get the flow-through volume function of valve closing , the time taken by the process is recorded as ; the flow rate in the stable stage of valve fully opening is recorded as ; Step B12: At different pressures, the valve core is opened with a 1 ms increment of the de-energization interval starting from 1 ms until the small flow valve seat has a tendency to open. The flow is integrated over time to obtain the flow-through volume function for the de-energization time t at the pressure difference P . The function of the required de-energization time t for the required flow-through volume is denoted as .

7. The pressure regulation method of claim 5, wherein, Step B3 specifically includes: calculating the flow volume required to pass through the large valve port in one operation. ,in, The pressure to be controlled until the end of control, i.e., the target pressure P. b Total required flow volume The small valve port is at the target pressure P b The flow volume within the next control cycle T, with K being a correction factor ≥ 2, ensures that at least two adjustment cycles are allowed for subsequent small valve ports, P b The target pressure is the pressure at the end of the control process.

8. The pressure regulation method of claim 5, wherein, The step B4 specifically includes: leaving the flow volume of the large valve port in the flow stabilization stage , wherein V l represents the flow volume required for one-time opening of the large valve port, P a is the pressure at the control start, P b is the pressure at the control end, i.e., the target pressure, V O (P a ) represents the flow volume function of the valve opening at the control start, V O (P b ) represents the flow volume function of the valve opening at the control end, and the average of the start and end stages is calculated , Q avg (P a ) represents the flow obtained by bringing P a into , Q avg (P b ) represents the flow obtained by bringing P b into ; the time required for the flow stabilization stage is , and the total time for one-time opening of the large valve port should be , wherein T O (P a ) represents the time experienced in the control start process, T O (P b ) represents the time experienced in the control end process, and the minimum volume of the flow is If the required volume is less than the minimum volume of the flow, the large valve port does not need to be opened to ensure the response speed, and the determination condition is recorded as .

9. The pressure regulation method of claim 5, wherein, The step B5 specifically comprises: Step B51: The outlet pressure P2 has not yet reached the target pressure P. b At that time, that is First, determine If the conditions are not met, the large valve port needs to be opened. At this time, the de-energization time of the solenoid valve is controlled. During this phase, maintain the power off and do not perform any operation, then restore power; if the conditions are met, proceed directly to step B52. Step B52: the outlet pressure P2 has not reached the target pressure P b , i.e. : the electromagnetic valve is controlled in cycles T, and the electromagnetic valve is powered off for , if t s > T, the electromagnetic valve is directly powered off for the whole cycle; wherein V ch (P b ) and V ch (P2) are calculated based on V ch (P), respectively. Step B53: Repeat B52 until Not satisfied.

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