Design method of electromagnetic valve with quick response of valve core, high-flow normally-open electromagnetic valve with springs connected in series and pressure regulation and control method of high-flow normally-open electromagnetic valve with springs connected in series

Abstract

The invention provides a design method of an electromagnetic valve with a quick response valve element, a large-flow normally-open electromagnetic valve with springs connected in series and a pressure regulation and control method of the large-flow normally-open electromagnetic valve. The electromagnetic valve comprises an electromagnetic coil, a valve shell, moving iron, the valve element, a small-flow valve seat, a large-flow valve seat, a first spring and a second spring. The valve element, the small-flow valve seat and the large-flow valve seat are sequentially arranged in the valve shell from top to bottom, the upper end of the valve element is connected with the moving iron, and the electromagnetic coil surrounds the moving iron and the valve shell. The first spring and the second spring are connected in series, and the first spring and the second spring are both connected with the small-flow valve seat and act on the upper end and the lower end of the small-flow valve seat. By means of the technical scheme, larger reset force of the small-flow valve seat can be achieved, the small-flow valve seat can be opened faster when the electromagnetic valve is powered off, and the large-flow response speed of the electromagnetic valve is higher.

Description

Technical Field

[0001] This invention relates to the field of solenoid valve technology, and in particular to the design method of a fast-response solenoid valve with valve core, a high-flow normally open solenoid valve with spring series connection, and its pressure regulation method. Background Technology

[0002] The patent application 202411225759.X, titled "Normally Open High-Flow Switching Solenoid Valve and Hydraulic Control Unit for Automotive Braking System," proposes a normally open high-flow solenoid valve. The main functions of this solenoid valve are: 1) When the solenoid coil is not energized, both the valve core and the small-flow valve seat remain open under spring force. At this time, the liquid from the upper and lower inlets can flow to the outlet through the small-flow and large-flow ports, thus fulfilling the normally open high-flow function of the solenoid valve; 2) When the solenoid coil is energized, the stationary iron is attracted to the moving iron under the influence 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 accumulates here, increasing the pressure at the upper end of the small-flow valve seat. Under this pressure, the small-flow valve seat moves downwards, closing... By closing the large flow valve port, and since the small flow valve port area is smaller than the large flow valve port, the two-stage closing method of first closing the small flow valve port and then closing the large flow valve port under the action of pressure difference can reduce the electromagnetic force required to close the solenoid valve, that is, reduce the current of the solenoid coil; 3) When the solenoid valve switches from energized to de-energized state, there is no longer an electromagnetic force between the moving iron and the stationary iron. The valve core is reset under the action of the spring, opening the small flow valve port. At this time, the high pressure fluid at the upper end of the small flow valve port will flow to the outlet through the small flow valve port, and the pressure at that point will drop until the downward force generated by the pressure at that point is less than the sum of the upward force generated by the high pressure fluid inside the lower inlet and the reset force of the second spring. At this time, the small flow valve seat moves upward, and the large flow valve port opens. This process is the two-stage reset process. Through the above design, the normally open, two-stage closing, and two-stage reset functions of the large flow normally open valve are realized, so that the on / off of the large flow hydraulic circuit can be controlled by a smaller electromagnetic force. However, this existing technology still has the following problems: it relies too heavily 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 solenoid valve; and the opening response speed of the small flow valve seat is slow when power is off. There is a stepped contact area between the small flow valve seat and the valve body. The main function of this area is to limit the highest position of the small flow valve seat and form a sealing area, dividing the small flow valve seat into two independent upper and lower regions. However, because liquid cannot enter this area, the fluid contact area above the small flow valve seat is much smaller than the fluid contact area below, which means that the closure of the small flow valve seat requires a greater upper pressure, making it more difficult for the small flow valve seat to close. Summary of the Invention

[0003] In view of this, the purpose of this invention is to provide a design method for a fast-response solenoid valve, a high-flow normally open solenoid valve with springs in series and its pressure regulation method, so as to achieve a greater reset force of the low-flow valve seat, so that the low-flow valve seat opens faster when the solenoid valve is de-energized, that is, the high-flow response speed of the solenoid valve is faster.

[0004] To achieve the above objectives, the present invention adopts the following technical solution: a design method for a fast-response solenoid valve, wherein the solenoid valve includes an electromagnetic coil, a valve body, a moving iron, a valve core, a small-flow valve seat, a large-flow valve seat, a first spring, and a second spring; the valve core, the small-flow valve seat, and the large-flow valve seat are arranged sequentially from top to bottom inside the valve body, the upper end of the valve core is connected to the moving iron, and the electromagnetic coil is arranged around the moving iron and the valve body; the first spring and the second spring are connected in series, and both the first spring and the second spring are connected to the small-flow valve seat and act on the upper and lower ends of the small-flow valve seat;

[0005] The design methodology includes the following steps:

[0006] Step A1: Calculate the variable data, including valve inlet pressure P1, valve outlet pressure P2, inlet equivalent area A1, small flow valve seat throttling orifice area A2, small flow valve seat upper acting area A3, small flow valve seat lower acting area A4, area A5 enclosed by the contact tangents of the small flow valve seat and the large flow valve seat, and the force F of the first spring when the valve is closed. s1 And the force F of the second spring when the valve is closed. s2 ;

[0007] Step A2: According to the throttling formula when both the input and output of a single-cavity valve are throttled, when the solenoid valve is de-energized, the valve core opens, and the pressure P in the space above the small-flow valve seat at this time... x Calculated as At this time, the pressure on the upper part of the valve seat for small flow is acting on the valve core, and the downward force of the valve seat for small flow is... Since the lower part of the small flow valve seat is directly connected to the inlet and the large valve port is closed at this time, the area of ​​action of the valve inlet pressure P1 is (A4-A5). Therefore, the downward force exerted by the lower pressure on the valve core on the small flow valve seat is... To ensure that the small-flow valve seat does not open simultaneously when the valve core opens, all downward forces acting on the large-flow valve seat must be greater than the upward forces. Then there is When the valve core opens, P2 will gradually increase and P1 will gradually decrease. If the condition is not met, the low-flow valve core will move upward, at which point the high-flow port of the solenoid valve will open.

[0008] The present invention also provides a high-flow normally open solenoid valve with springs in series. Based on the design method of the valve core fast-response solenoid valve, the upper and lower ends of the low-flow valve seat are respectively an upper cylindrical protrusion and a lower cylindrical protrusion. The upper cylindrical protrusion is connected to the first spring, and the lower cylindrical protrusion is connected to the second spring.

[0009] The upper end of the small flow valve seat is provided with a circumferential side guide, or the side of the small flow valve seat is provided with a side guide, and the inner side of the side guide forms a groove for accommodating the first spring.

[0010] In a preferred embodiment, a first liquid guiding groove is provided inside the valve housing facing the small flow valve seat, and multiple first liquid guiding grooves are evenly arranged along the circumference of the valve housing.

[0011] In a preferred embodiment, the portion of the low-flow valve seat facing the valve housing is provided with a plurality of second liquid guiding grooves, and the plurality of second liquid guiding grooves are evenly arranged along the circumference of the low-flow valve seat.

[0012] This invention also provides a pressure regulation method based on the aforementioned high-flow normally open solenoid valve connected in series with a spring, comprising the following steps:

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

[0014] Step B2: Calculate the initial volume V based on the PV characteristic curve. a The target volume is V b ;

[0015] Step B3: Calculate the flow volume required to open the large valve port in one go;

[0016] Step B4: Calculate the flow volume reserved for the large valve orifice during the steady flow phase, and compare the required volume with the minimum flow volume;

[0017] Step B5: Propose pressure control logic.

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

[0019] Step B11: Measure the pressure difference P and flow rate Q at the valve inlet and outlet. Control the valve in a energized-de-energized sequence to obtain the correlation between flow rate and time. Repeat the above process under different pressure differences P to obtain a set of flow rate-time curves related to pressure P. Integrate the flow rate before reaching a stable high flow rate over time to obtain the flow volume function when the valve is open. 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 , among which, T O (P a T represents the time elapsed during the control start process. O (P b () indicates the time elapsed during the control termination process, and the minimum flow volume is... If the required volume is less than the minimum flow volume, then the large valve does not need to be opened to ensure response speed. This condition is denoted as... .

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

[0024] 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.

[0025] Step B52: The outlet pressure P2 has not yet reached the target pressure P. b At that time, that is The control is performed in a cycle T, and the solenoid valve is de-energized for a period of time in each cycle. If t s If T >, then the solenoid valve is completely de-energized during that cycle; where V ch (P b V ch (P2) based on V respectively ch (P) is calculated;

[0026] Step B53: Repeat B52 until... Not satisfied.

[0027] Compared with the prior art, the present invention has the following advantages: 1) When designing the liquid flow channel, the required 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 larger reset force of the small flow valve seat 4 can be designed, so that the small flow valve seat opens faster when the solenoid valve is de-energized, that is, the large flow response speed of the solenoid 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 electromagnetic force. This allows the design value of the first spring (including pre-pressure, spring stiffness, etc.) to be adjusted arbitrarily 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 decreasing the pre-pressure or stiffness of the first spring. Attached Figure Description

[0028] Figure 1 This is a schematic cross-sectional view of the solenoid valve according to a preferred embodiment of the present invention;

[0029] Figure 2 This is a schematic diagram of the second side guide position relationship according to a preferred embodiment of the present invention;

[0030] Figure 3 This is a schematic diagram showing the relationship of the first liquid guiding groove in a preferred embodiment of the present invention;

[0031] Figure 4 This is a schematic diagram of the first liquid guiding groove outside the overlapping area of ​​the small flow valve seat and valve body in a preferred embodiment of the present invention;

[0032] Figure 5 This is a schematic diagram of the relationship between the second liquid guiding grooves in a preferred embodiment of the present invention;

[0033] Figure 6 This is a schematic diagram of the second liquid guiding groove within the overlapping area of ​​the small flow valve seat and valve body in a preferred embodiment of the present invention;

[0034] Figure 7 This is a schematic diagram showing the positions of each variable in step A1 of a preferred embodiment of the present invention;

[0035] Figure 8 The energizing time-flow rate curve is a preferred embodiment of the present invention;

[0036] Figure 9 The pressure (P)-volume (V) curve is a preferred embodiment of the present invention. Detailed Implementation

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

[0038] It should be noted that the following detailed descriptions are illustrative and intended to provide further explanation of this application. Unless otherwise specified, 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 pertains.

[0039] It should be noted that the terminology used herein is for the purpose of describing particular implementations only and is not intended to limit the exemplary implementations according to this application; as used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise; furthermore, it should be understood that when the terms “comprising” and / or “including” are used in this specification, they indicate the presence of features, steps, operations, devices, components and / or combinations thereof.

[0040] refer to Figure 1-9The design method of a fast-response solenoid valve with valve core 3 is described. The solenoid valve includes an electromagnetic coil, a valve body 1, a moving iron 2, a valve core 3, a small-flow valve seat 4, a large-flow valve seat 5, a first spring 6, and a second spring 7. The valve core 3, the small-flow valve seat 4, and the large-flow valve seat 5 are arranged sequentially from top to bottom inside the valve body 1. The upper end of the valve core 3 is connected to the moving iron 2, and the electromagnetic coil surrounds the moving iron 2 and the valve body 1. The positional relationship of the electromagnetic coil, valve body 1, moving iron 2, valve core 3, small-flow valve seat 4, and large-flow valve seat 5 is consistent with the solenoid valve structure disclosed in patent application CN119196102A. The difference is that in this application, the first spring 6 and the second spring 7 are connected in series, and both the first spring 6 and the second spring 7 are connected to the small-flow valve seat 4. The springs are connected 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 an upper cylindrical protrusion and a lower cylindrical protrusion. The upper cylindrical protrusion is connected to the first spring 6, and the lower cylindrical protrusion is connected to the second spring 7, which can prevent the spring from shaking or tilting. The main advantage of the series connection of springs 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 closes the small flow valve seat 4 is the downward electromagnetic force plus the downward force generated by the pressure difference between the upper and lower ends of the small flow valve seat 4. It only needs to be greater than the reset force of the second spring 7 to close the small flow valve seat 4. Compared with the comparative technology, which only has the downward force generated by the pressure difference between the upper and lower ends of the small flow valve seat 4, the force in this application is greater, which means that it is easier to close the small flow valve seat 4.

[0041] like Figure 1 As shown, in order to ensure that the small flow valve seat 4 does not shake when moving up and down in the valve body 1, the first side 41 of the small flow valve seat 4 is used as a guide for the valve body 1.

[0042] remove Figure 1 In addition to the side guide shown, a method such as Figure 2 The design of the upper side guide shown depicts a second side guide 42 circumferentially arranged at the upper end of the small flow valve seat 4. A groove is formed on the inner side of the second side guide 42 to accommodate the first spring 6, thus allowing the side of the groove to serve as a guide for the valve body 1. By arranging the first spring 6 within the groove at the upper part of the small flow valve seat 4, the side of the upper groove can also serve as a guide for the valve body 1. This method reduces... Figure 1 The side guide shown may scratch the lower inlet, reducing the design difficulty.

[0043] To solve the problem of unstable closure of valve seat 4 in low-flow conditions, a design is made as follows: Figure 3-4As shown, a first liquid guiding groove 11 is provided inside the valve housing 1 facing the small flow valve seat 4. Multiple first liquid guiding grooves 11 are evenly arranged along the circumference of the valve housing 1, allowing liquid below the small flow valve seat 4 to act on the upper part of the small flow valve seat 4 through the first liquid guiding grooves 11. This reduces the equivalent action area of ​​the fluid on the lower surface of the small flow valve seat 4 (because the pressure at the first liquid guiding groove 11 on the upper and lower surfaces is equal, the forces generated by the pressure cancel each other out, directly leading to a reduction in the action area), thus reducing the upper pressure required for the small flow valve seat 4 to close. This measure reduces the pressure requirement while retaining the limiting function, and still has a certain overlap area to ensure a seal.

[0044] Based on this idea, such as Figure 5-6 As shown, an external groove can also be formed on the small flow valve seat 4, that is, multiple second liquid guiding grooves 43 can be provided on the part of the small flow valve seat 4 facing the valve housing 1. Multiple second liquid guiding grooves 43 are evenly arranged along the circumference of the small flow valve seat 4 to achieve the same effect. This can be freely selected according to manufacturing process requirements. Figure 3 or Figure 5 The structure shown.

[0045] The design method of the fast-response solenoid valve with valve core 3 includes the following steps:

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

[0047] Step A2: According to the throttling formula when both the input and output of a single-cavity valve are throttled, when the solenoid valve is de-energized, the valve core 3 opens, and at this time the pressure P in the space above the small-flow valve seat 4 is... x Calculated as At this time, the pressure on the upper part of the valve core 3 and the small flow valve seat 4 acts on the valve core 3, and the downward force of the small flow valve seat 4 is... Since the lower part of the small flow valve seat 4 is directly connected to the inlet and the large valve port is closed, the pressure at the lower part is P1. The area of ​​action of the lower pressure is (A4-A5). Therefore, the upward force exerted by the lower pressure on the valve core 3 and the small flow valve seat 4 is... To ensure that the small-flow valve seat 4 does not open simultaneously when valve core 3 opens, all downward forces acting on the large-flow valve seat 5 must be greater than upward forces. Then there is 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 can be obtained by integrating the flow rate with respect to 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 based on the PV characteristic curve. a The target volume is V b ;

[0055] Step 3: Calculate the flow volume required to open the large valve port in one go. ,in To control 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, where K is 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.

[0056] Step 4: Calculate the flow volume reserved for the large valve orifice during the steady-flow 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 The expression represents the flow volume function of the valve opening at the end of the control phase. Since the pressure changes continuously during the flow phase, the flow velocity in this phase is simply calculated as the average of the beginning and end phases. The duration of the stable traffic phase is then... The total time for the large valve to open once should be , among which, T O (P a T represents the time elapsed during the control start process. O (P b ) represents the time elapsed during the control termination process. In the above calculation, t s When the value is 0, it represents the minimum time from opening to closing the large valve port; at this time, the minimum flow volume is... If the required volume is less than the minimum flow volume, then the large valve does not need to be opened to ensure response speed. This condition is denoted as... .

[0057] Step B5: Pressure Control Logic

[0058] 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.

[0059] Step B52: The outlet pressure P2 has not yet reached the target pressure P. b At that time, that is The control is performed in a cycle T, and the solenoid valve is de-energized for a period of time in each cycle. If t s If T >, then the solenoid valve will be completely de-energized during that cycle;

[0060] Step B53: Repeat B52 until... Not satisfied.

Claims

1. A design method for a fast-response solenoid valve, the solenoid valve comprising an electromagnetic coil, a valve body, a moving iron, a valve core, a small-flow valve seat, a large-flow valve seat, a first spring, and a second spring; the valve core, the small-flow valve seat, and the large-flow valve seat are arranged sequentially from top to bottom inside the valve body, the upper end of the valve core is connected to the moving iron, and the electromagnetic coil is arranged around the moving iron and the valve body; characterized in that, The first spring and the second spring are connected in series. Both the first spring and the second spring are connected to the small flow valve seat and act on the upper and lower ends of the small flow valve seat. The design methodology includes the following steps: Step A1: Calculate the variable data, including valve inlet pressure P1, valve outlet pressure P2, inlet equivalent area A1, small flow valve seat throttling orifice area A2, small flow valve seat upper acting area A3, small flow valve seat lower acting area A4, area A5 enclosed by the contact tangents of the small flow valve seat and the large flow valve seat, and the force F of the first spring when the valve is closed. s1 And the force F of the second spring when the valve is closed. s2 ; Step A2: According to the throttling formula when both the input and output of a single-cavity valve are throttled, when the solenoid valve is de-energized, the valve core opens, and the pressure P in the space above the small-flow valve seat at this time... x Calculated as At this time, the pressure on the upper part of the valve seat for small flow is acting on the valve core, and the downward force of the valve seat for small flow is... Since the lower part of the small flow valve seat is directly connected to the inlet and the large valve port is closed at this time, the area of ​​action of the valve inlet pressure P1 is (A4-A5). Therefore, the downward force exerted by the lower pressure on the valve core on the small flow valve seat is... To ensure that the small-flow valve seat does not open simultaneously when the valve core opens, all downward forces acting on the large-flow valve seat must be greater than the upward forces. Then there is When the valve core opens, P2 will gradually increase and P1 will gradually decrease. If the condition is not met, the low-flow valve core will move upward, at which point the high-flow port of the solenoid valve will open.

2. A high-flow normally open solenoid valve with springs connected in series, characterized in that, Based on the design method of the valve core fast response solenoid valve according to claim 1, 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 to the first spring, and the lower cylindrical protrusion is connected to the second spring. The upper end of the small flow valve seat is provided with a circumferential side guide, or the side of the small flow valve seat is provided with a side guide, and the inner side of the side guide forms a groove for accommodating the first spring.

3. The high-flow normally open solenoid valve with spring series connection according to claim 2, characterized in that, A first liquid guiding groove is provided inside the valve housing facing the small flow valve seat, and multiple first liquid guiding grooves are evenly arranged along the circumference of the valve housing.

4. The high-flow normally open solenoid valve with springs in series according to claim 2, characterized in that, The portion of the low-flow valve seat facing the valve housing is provided with a plurality of second liquid guiding grooves, and the plurality of second liquid guiding grooves are evenly arranged along the circumference of the low-flow valve seat.

5. A pressure control method, characterized in that, The high-flow normally open solenoid valve based on any one of claims 2-4, with springs connected in series, includes the following steps: Step B1: Obtain the PV characteristic curve of the controlled cavity, denoted as... Where P is the pressure difference between the valve inlet and outlet, and V is the pressure difference between the valve outlet and the inlet. ch (P) represents the volume curve, i.e. the conversion relationship between pressure P and volume; Step B2: Calculate the initial volume V based on the PV characteristic curve. a The target volume is V b ; Step B3: Calculate the flow volume required to open the large valve port in one go; Step B4: Calculate the flow volume reserved for the large valve orifice during the steady flow phase, and compare the required volume with the minimum flow volume; Step B5: Propose pressure control logic.

6. The pressure regulation method according to claim 5, characterized in that, Step B1 specifically includes: Step B11: Measure the pressure difference P and flow rate Q at the valve inlet and outlet. Control the valve in a energized-de-energized sequence to obtain the correlation between flow rate and time. Repeat the above process under different pressure differences P to obtain a set of flow rate-time curves related to pressure P. Integrate the flow rate before reaching a stable high flow rate over time to obtain the flow volume function when the valve is open. 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 . ; 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: .

7. The pressure regulation method according to claim 5, characterized in that, 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 according to claim 5, characterized in that, Step B4 specifically includes: reserving the 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 , among which, T O (P a T represents the time elapsed during the control start process. O (P b () indicates the time elapsed during the control termination process, and the minimum flow volume is... If the required volume is less than the minimum flow volume, then the large valve does not need to be opened to ensure response speed. This condition is denoted as... .

9. The pressure regulation method according to claim 5, characterized in that, Step B5 specifically includes: 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 yet reached the target pressure P. b At that time, that is The control is performed in a cycle T, and the solenoid valve is de-energized for a period of time in each cycle. If t s If T >, then the solenoid valve is completely de-energized during that cycle; where V ch (P b V ch (P2) based on V respectively ch (P) is calculated; Step B53: Repeat B52 until... Not satisfied.

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