Micro-mechanical cushion valve

Abstract

This invention provides a micro-mechanical buffer valve. An internal flow channel of the buffer valve includes an inner micro-orifice, an inner chamber, an outer orifice, and a floating ball. The internal flow channel connects to an internal pressure chamber and also to a gas connector of an external high-pressure gas source. The buffer valve structure includes a breather, a micro-valve body, and the floating ball. During operation, the buffer valve has the following functions: a high-filling action, a shielding action, a release action (including a release mechanism), a shielding time Δt, and an adjustment mechanism. The micro-valve body comprises an inner chamber, an outer chamber, an isolation section, and an outer orifice. During gas discharge, the high-pressure gas in the pressure chamber is rapidly released. The floating ball floats with the airflow towards the outer orifice and shields it, reducing the discharge velocity of the depressurized gas and minimizing vibrations caused by the high-pressure gas discharge.

Description

Technical Field

[0001] This invention relates to a buffer valve, which is a bidirectional valve installed on the breather port of a pneumatic diaphragm valve for conveying high-cleanliness fluids. The pneumatic diaphragm valve has a diaphragm and a valve seat. The buffer valve can slow down the opening and closing action of the pneumatic diaphragm valve to reduce the impact of the closing of a central portion of the diaphragm with the valve seat and the vibration caused by the rapid release of high-pressure gas. Such impacts and vibrations can increase material peeling and cause contamination. In recent years, wafer grinding has further pursued the goal of preventing suspended particles in the conveyed liquid from generating impact jets due to the closing of the central portion and the valve seat. In addition, the rapid release of high-pressure gas causes the movement trajectory of suspended particles to separate from the fluid direction, resulting in collisions and agglomeration. Background Technology

[0002] The pneumatic diaphragm valve includes a pneumatic cylinder, a diaphragm, a valve seat, etc. The pneumatic cylinder is divided into a pneumatic chamber and a spring chamber by a piston. The spring chamber is equipped with a spring. The spring chamber and the pneumatic chamber are respectively provided with a breather hole. The breather hole of the pneumatic chamber can be filled with high-pressure gas, which is usually between 3 bar and 7 bar. The conventional diaphragm has a monolithic structure comprising a circumferential portion, a central portion, and an elastic portion. The cross-sectional shape of the elastic portion is similar to an Ω-shaped arc curve with a longer curve length. This arc curve surrounds a central axis, forming an annular curved surface structure with a central hole. The outer circumference of the elastic portion connects to the circumferential portion, and the periphery of the center connects to the central portion. This arc curve has more stretching space but a lower elongation ratio. When the central portion moves, the arc curve can provide more deformation and stretching, allowing the central portion to move more and faster. Its lower elongation ratio brings a longer lifespan to the diaphragm. At the same time, the movement of the central portion pulls the elastic portion, which has a smaller diameter area, allowing the elastic portion to withstand less fluid pressure without reducing the movement speed of the central portion. Another diaphragm structure has an elastic portion that is a concave spherical structure shaped like a lid, with a shorter curve length and a higher elongation ratio. When the central portion moves, this curve can provide a larger area of ​​deformation and stretching to maintain the displacement of the central portion. Its higher elongation ratio brings a slightly shorter lifespan to the diaphragm.The pneumatic diaphragm valve comes in two types: normally closed and normally open. In a normally closed valve, the central portion is tightly closed by the spring force within the spring chamber, ensuring close contact with the valve seat. For example, in a 1-inch valve, the spring force would be 70 kg. In a normally open valve, the central portion is separated from the valve seat by the spring force within the spring chamber, maintaining its open position. For example, in a 1-inch valve, the spring tension would be 30 kg. The air chamber in a normally closed valve is located behind the diaphragm, and the spring chamber in a normally open valve is also located behind the diaphragm. Both air chambers are filled with high-pressure gas to push the piston, compressing the spring. When a normally closed valve opens, the central portion moves away from the valve seat; when a normally open valve closes, the central portion moves away from the valve seat. The valve seat has a proximity speed. When these two types of valves perform such actions, the more the spring in the spring chamber is compressed, the higher the rebound force will be. This rebound force can provide a good buffering effect and will not cause too much impact. The pressure chamber withstands the gradually increasing pressure, which reduces the vibration of high-pressure gas. At the moment of filling with high-pressure air, the piston will not move rapidly, so that when the central part moves away from the valve seat, only a slight vacuum negative pressure phenomenon will be generated. When the high-pressure gas is released, the pressure in the pressure chamber drops sharply, which will cause the vibration of high-pressure gas release. The pressure in the exhaust pipe is usually one atmosphere, and the absolute pressure is 1 bar. The compression ratio of absolute pressure = high-pressure gas pressure / exhaust pipe pressure. When the compression ratio of high-pressure gas release is >1.5 times, ultrasonic waves will be generated. The violent vibration, coupled with the spring releasing its compressed rebound force to push the piston, causes it to move too quickly. For normally closed valves, this excessively rapid approach speed of the central section can impact the valve seat. For normally open valves, the excessively rapid separation speed of the central section can create a brief negative pressure vacuum on the valve seat. In normally closed valves, during gas discharge, the central section impacts the valve seat at a high approach speed. The curved shape of the elastic part cannot provide sufficient buffering effect from the liquid pressure. This closure process generates a water hammer effect, which not only produces a jet of water but also transmits pressure waves upstream and downstream along the pipeline, causing damage to other equipment or joints in the pipeline, or releasing unwanted particles. This can contaminate clean liquids. For normally open valves, during gas discharge, the central part moves away from the valve seat at a high speed, and the arc curve of the elastic part moves sharply upward. The fluid being transported cannot be replenished in a short time, resulting in a brief negative pressure effect near the valve seat. This causes the fluid in the diaphragm to generate brief and intense turbulence and eddies. These fluids generate intense phenomena when the valve is opened and closed, such as jets, turbulence, and eddies. In semiconductor manufacturing processes, in addition to the material particles generated by the impact between the central part and the valve seat, unwanted particles are also released upstream and downstream of the pipeline, damaging the pipeline equipment. Furthermore, liquids containing suspended abrasives can cause the direction of particle movement to be inconsistent with the direction of the fluid, leading to the problem of particle collisions generating static electricity and agglomeration.

[0003] Based on the above description, the basic application requirements of the pneumatic diaphragm valve for conveying high-purity fluids of the present invention can be categorized into the following two issues:

[0004] Problem 1: The fluid being transported will not be affected by the excessively fast approach speed of the central section and the valve seat closing, which will cause the jetting effect of water droplets and the vibration of pressure waves transmitted upstream and downstream in the pipeline, or by the excessively fast separation speed of the central section and the valve seat, which will cause brief and intense turbulence and eddies.

[0005] Question 2: When the high-pressure gas is discharged through the pressure chamber of the diaphragm valve, it will not produce violent vibrations or shock waves that propagate upstream and downstream in the liquid delivery pipe.

[0006] If these two problems can be solved at the same time, then the following requirements one, two and three can be satisfied simultaneously, because each problem involves requirements one, two and three.

[0007] Requirement 1: Reduce the release of particles.

[0008] Requirement 2: Reduce damage to pipe joints and devices, especially reduce the risk of leakage.

[0009] Requirement 3: Reduce the agglomeration of suspended particles.

[0010] Requirement 4: Adjustment of the opening and closing time of the diaphragm valve.

[0011] The third requirement is a new requirement arising from the latest semiconductor manufacturing process requirements. The fourth requirement is to provide more adjustments to the length of operation time for different processes when solving the problems of the first and second requirements.

[0012] In the prior art, several reference solutions have been proposed for both Problem 1 and Problem 2. These reference solutions aim to satisfy Requirements 1, 2, 3, and 4. The following are the reference solutions of the prior art:

[0013] Case Study 1

[0014] The 1998 US patent, US5779224A - Poppet valve, addresses problem one by attempting to resolve the impact between the central section and the valve seat. A solution involving adding a soft rubber pad to the back of the diaphragm is proposed. However, this pad only protects the diaphragm itself and does not address the issue of violent vibrations caused by the release of high-pressure gas. Therefore, it fails to solve problem two. Another solution involves installing a low-force auxiliary spring in the normally closed diaphragm valve's pressure chamber to allow for a smoother, buffered closure. This supposedly significantly reduces the impact between the central section and the valve seat, resulting in less vibration and fewer released particles. However, it doesn't specify the percentage reduction in approach velocity due to the reduced impact, meaning it may not fully resolve problem one, and the fluid jetting issue cannot be definitively confirmed.

[0015] Reference Case 2

[0016] In 1999, US Patent 5865423A, "High Flow Diaphragm Valve," addressed the problem of water hammer and jetting. It proposed a solution by shaping a valve chamber surrounding the valve seat into a bowl shape, with the elastic portion of the matching diaphragm also shaped like a lid. Compared to an Ω-shaped structure, its cross-sectional curve length is shorter. Movement of the central portion pulls a larger diameter elastic portion, thus, in practice, the valve chamber has a larger outer diameter, allowing the diaphragm to have a larger diameter to withstand deformation. This larger diameter elastic portion can withstand more fluid pressure. When the central portion moves towards the valve seat, the diaphragm has a larger area to withstand the fluid pressure, reducing its approach velocity. Furthermore, the bowl-shaped valve chamber can achieve a larger flow rate when open. In 2000, US Patent 6123320A, "Sanitary..." The diaphragm valve also has a similar bowl-shaped valve chamber structure, and the elastic part of its diaphragm is also shaped like a pot lid. However, in the test, it did not significantly reduce the approach speed or mitigate the vibration caused by the release of high-pressure gas. In other words, it did not completely solve the first problem: the fluid jetting problem could not be solved. Secondly, it did not solve the second problem: the vibration problem caused by the release of high-pressure gas.

[0017] Reference Case 3

[0018] The 1997 Japanese patent, JPH09217845(A) Diaphragm Valve, addresses problem one by installing an auxiliary spring with a low elasticity in the air pressure chamber of a normally closed diaphragm valve. The normally closed spring above the piston ensures that the diaphragm can be pressed against the valve seat, while the auxiliary spring below the piston allows the diaphragm to close smoothly and buffered. This significantly reduces the impact between the central part and the valve seat, resulting in less vibration and fewer particles being released. However, it does not mention the percentage reduction in approach velocity due to the reduced impact, meaning that problem one may not be completely solved, and it cannot be confirmed that the fluid jetting problem has been resolved. Furthermore, problem two remains unresolved: the high-pressure air is still not slowed down during release, resulting in violent vibrations.

[0019] Reference Case 4

[0020] Japanese Patent JP2009180338(A)-FLUID CONTROL VALVE AND OPERATION AIRINTERMEDIATE VALVE, 2009, introduces a micro-valve mechanism to further improve the problem. The micro-valve mechanism includes a micro-orifice, a micro-piston, a micro-spring, a micro-sealing surface, and a micro-fixed seat. The micro-piston has a micro-flange on the opening side of the micro-fixed seat. The micro-spring is mounted on the outer annular surface of the micro-piston and is confined inside the micro-fixed seat by the micro-flange. A small portion of the micro-piston protrudes from the outlet side of the micro-fixed seat. The micro-piston can seal with the micro-sealing surface, which is mounted inside the air pressure chamber. The micro-orifice is mounted on the micro-piston and communicates with the internal space of the micro-fixed seat. The micro-fixed seat has a through hole that communicates with the space of the air pressure chamber.

[0021] In the first embodiment, the micro-fixed seat is mounted on the piston and located on one side of the pressure chamber, allowing it to move up and down with the piston. When the piston is in the open valve position, the micro-valve mechanism moves with the piston to the open valve position without obstructing the vent hole, and the micro-piston does not engage with the micro-sealing surface for sealing. When the piston is in the closed valve position, the micro-fixed seat moves with the piston to the valve position, and the opening surface of the fixed seat contacts the inner surface of the pressure chamber located on the valve seat side, and the micro-piston completely seals the micro-sealing surface and the vent hole. When the piston is in the closed valve position, and high-pressure gas is started to fill the vent hole to open the valve, the high-pressure gas will first pass through the micro-piston. The micro-orifice of the valve restricts the gas flow. As the pressure chamber gradually increases, the piston moves toward the spring chamber and compresses the spring. At this time, the micro-mechanism also moves and allows the vent to accelerate the filling of gas. When the valve is in the open position, the pressure chamber is completely filled with high-pressure gas and the piston completely suppresses the spring in the spring chamber. When the valve is to be switched from the open position to the closed position, the micro-mechanism will gradually cover the vent until it is completely covered when it approaches the micro-sealing surface. Initially, the release of high-pressure gas is not affected by the micro-mechanism. As the vent is gradually covered, the micro-orifice will restrict the flow of the released residual high-pressure gas.

[0022] In the second embodiment, the micro valve mechanism is installed inside the vent of the pressure chamber and is linked to the opening and closing of the valve. When the piston is in the open position, the micro spring of the micro valve mechanism lifts the micro piston without blocking the vent. When the open valve is to be switched to the closed position, the high-pressure gas will first flow through the vent into the fixed seat and then into the vent. At this time, the airflow is released in an almost unlimited manner. When the central part approaches the valve seat, the surface of the piston will contact and press the micro piston to move until it contacts and seals the sealing surface. Only then does the gas flow limit function occur.

[0023] In the two embodiments above, the piston initially moves at a normal speed and acceleration. As the breather hole is gradually blocked, the piston stops accelerating and gradually decelerates. However, due to the continuous action of the spring force and the momentum of the piston, the central part of the diaphragm still impacts the valve seat when the valve is closed. This still does not solve problem one: the water hammer and jet problem between the central part and the valve seat. In the initial stage of releasing high-pressure gas in the pressure chamber, the high-pressure gas flows directly out of the breather hole, causing violent vibrations from the gas release. The violent vibrations only subside when the breather hole is gradually blocked. This high-pressure gas release process still does not solve problem two: the problem of violent vibrations caused by high-pressure gas. The micro-valve mechanism is linked to the valve opening and closing mechanism and lacks adjustment and improvement space for the stroke timing, which basically cannot meet requirement four: the opening and closing time of the diaphragm valve must meet the requirements.

[0024] Reference Case 5

[0025] A 2020 Taiwan patent, TW202010966A - Diaphragm valve structure, addresses problems one and two. It relates to a diaphragm valve structure for use in perfluoropolymer diaphragms operating at 200°C. Regarding the particulate-free release structure, it mentions that the piston portion includes an annular section, a lower annular rib, an upper annular rib, and a damping ring. The upper valve body is mounted inside the annular section and has a centrally conical, open cup-shaped structure with an outer annular surface, a clamping portion, a shaft hole, a first annular groove, a second annular groove, and a diaphragm chamber. The damping ring is coupled to the first annular groove. The dimensions of the diaphragm are in a sliding fit, which provides a damping effect to reduce vibration when the diaphragm moves up and down; the lower annular rib is coupled with the second annular groove, and the dimensions of the two are in a sliding fit, which provides a damping effect to reduce vibration when the diaphragm moves up and down. This is to reduce vibration by slowing down the release of gas. However, since the means is to achieve this by using structural conditions, it is not possible to further adjust the vibration reduction conditions according to the requirements, and it cannot meet requirement four. The opening and closing time of the diaphragm valve must meet the requirements, and the variation of structural dimensional tolerances will reduce the effect of controlling the release of gas.

[0026] Reference Case Six

[0027] Taiwan Patent No. TW202045845-FLUID CONTROL VALVE, issued in 2020, addresses the solutions to problems one and two. The method in this reference is similar to but slightly different from that in Reference No. 4. A fluid control valve has a pneumatic cylinder, which is divided into a pressure chamber and a spring chamber by a piston. The spring chamber is equipped with a spring. The spring chamber and the pressure chamber are each provided with a breather hole. The breather hole of the pressure chamber can be used to fill high-pressure gas. When the piston is in the open valve position, the pressure chamber contains fluid. The fluid is discharged through the breather hole when the piston moves toward the closed valve position.

[0028] In the first embodiment, a throttling section is installed on one side of the pressure chamber and can move up and down with the piston. The throttling section can be an annular structure, with a flow path having a smaller cross-sectional area than the breather hole formed between the throttling section and the inner wall of the pressure chamber. Alternatively, a flow-limiting slit can be installed on the flow-limiting section. When the piston is in the open valve position, the throttling section does not block the breather hole; when the piston is in the closed valve position, the throttling section completely blocks the breather hole. When the piston is in the closed valve position, and high-pressure gas is started to fill the breather hole to open the valve, the high-pressure gas first passes through the flow-limiting channel and its flow rate is restricted. As the pressure in the pressure chamber gradually increases, the piston moves towards the spring chamber and compresses the spring, at which point the flow-limiting... The flow path also moves, exposing a larger cross-sectional area of ​​the breather to accelerate gas filling. When the valve is in the open position, the pressure chamber is completely filled with high-pressure gas, and the piston completely suppresses the spring in the spring chamber. When the valve is to be changed from the open position to the closed position, the throttling part will gradually block the breather until it is completely blocked. Initially, the high-pressure gas is not affected by the flow restriction part. As the breather is gradually blocked, the flow restriction path will restrict the release of high-pressure gas. That is, the piston will move at normal speed and acceleration. As the breather is gradually blocked, the piston no longer accelerates but gradually decelerates. However, the spring force continues to act, and the momentum of the piston means that in the closed position, the central part of the diaphragm will still impact the valve seat. This still doesn't solve problem one: the water hammer and jetting issues between the central part and the valve seat. When high-pressure gas is initially released from the pressure chamber, it first flows through the breather hole, which is not blocked by the flow-limiting slit, causing violent vibrations during gas release. These vibrations only subside as the breather hole is gradually blocked by the throttling section, until the breather hole is completely blocked by the slit. This high-pressure gas release process still doesn't solve problem two: the violent vibrations caused by the high-pressure gas. The flow-limiting slit and the flow-limiting channel are constructed with fixed structural gaps or slits, lacking adjustment and improvement space, and essentially failing to meet requirement four: the opening and closing time of the diaphragm valve must meet the requirements. The throttling section in the first embodiment also... This can be used in normally open valves, where the throttling section is installed in the spring chamber. When the pressure chamber is filled with high-pressure gas, it can restrict the gas from flowing out of the spring chamber slowly, allowing the central part of the diaphragm to approach the valve seat at a slow moving speed. However, because the pressure in the spring chamber is only one atmosphere, the scarce air quality is not very effective. The buffering effect of the pressure chamber filled with high-pressure gas is mostly still borne by the spring. Furthermore, when the high-pressure gas in the pressure chamber is released to open the valve, the vibration caused by the rapid release of the high-pressure gas cannot solve the second problem. Moreover, the spring pushes the piston, causing the central part to move at a high speed, resulting in a brief period of negative pressure, turbulence, and eddies near the valve seat. Such situations are not appropriate solutions to problems one and two.This reference design also relies on structure to achieve the countermeasures, making it difficult to meet requirement four. Furthermore, variations in structural dimensional tolerances will diminish the effectiveness of controlling gas release.

[0029] The analysis of the six reference cases above reveals that none of them provide complete solutions to problems one and two. Reference cases one and three include a spring in the pressure chamber, which can buffer the impact of the central part on the valve seat, but they still do not address the vibration when high-pressure gas is released from the pressure chamber. Furthermore, requirement four requires an adjustable mechanism. Reference cases four, five, and six are all linked to the opening and closing of the valve. When the high-pressure gas in the pressure chamber is not released, the spring in the spring chamber has maximum compression. Taking a 1-inch valve as an example, the compression force is as high as 70 kg and the gas pressure is above 5 bar. When the high-pressure gas in the pressure chamber is to be released, the high-pressure gas will be released in an infinite flow manner, resulting in maximum gas vibration. When the internal high pressure and the external pipeline air pressure ratio are greater than 1.5, ultrasonic knocking will occur, and the spring energy stored in the spring will be released in large quantities at the same time. At this time, the spring force will push the piston to move at the fastest speed. The diaphragm valve will be subjected to a lot of vibration. When the central part approaches the valve seat, the piston will decelerate sharply. The air cushion damping effect comes from the flow restriction of the discharged gas, but the entire valve body still needs to bear the vibration of deceleration. At this time, the air cushion deceleration function is expected to provide shock absorption. The whole process is that the maximum vibration is generated by gas release and spring acceleration, and shock absorption is only expected during deceleration. This cannot achieve the function of full-process shock absorption, so it cannot completely solve problems one and two, nor can it meet requirement four.

[0030] Reference 4 introduces a miniature valve mechanism, but it does not improve the above problems and lacks the adjustment requirement for the opening and closing time of the diaphragm valve, which is requirement 4. The above references cannot meet the vibration control requirements during the process of the normally closed valve changing from the open state to the closed state, that is, they cannot meet problems 1 and 2, but cannot meet requirements 1, 2, 3, and 4.

[0031] During the process of a normally open valve changing from the closed state to the open state, when the pressure chamber releases high-pressure gas, there is a violent ultrasonic vibration at the moment of release.

[0032] Regarding Case 4, it is currently impossible for this miniature valve mechanism to effectively and immediately alleviate the high-pressure gas release from normally closed and normally open valves, reduce the release of the spring force, and continue venting. Furthermore, it cannot ensure that the central part of the normally open valve moves away from the valve seat at a reasonable speed to reduce turbulence, backflow, and negative pressure near the valve seat. Similarly, it cannot ensure that the central part of the normally closed valve approaches the valve seat at a reasonable speed to reduce jetting near the valve seat. It is also questionable whether it can quickly discharge residual gas when the pressure decreases, allowing the valve to close smoothly and saving the entire stroke.

[0033] Based on the above description, this miniature valve mechanism must further address the following issues for the entire process from the open valve state to the closed valve state, or from the closed valve state to the open valve state:

[0034] Question 3: When high-pressure gas is released, there should be an immediate reaction to slow down the release of high-pressure gas and reduce the extension speed of the spring in the spring chamber.

[0035] Question 4: When the pressure of the high-pressure gas decreases, the residual gas in the pressure chamber can be quickly discharged.

[0036] Question 5: When filling the pressure chamber with high-pressure gas, the gas filling speed is not affected.

[0037] The miniature valve mechanism proposed in Reference 4 is very similar to a common check valve with a spring mechanism, including a valve structure with a movable ball or micro-piston, or with the addition of a spring. The most common of these mechanisms is the ball check valve, while in the prior art, many types of float check valves have been proposed. The following are reference solutions of the prior art:

[0038] Reference Case Seven

[0039] European Patent EP0192474A2-A valve (1986) is a check valve for engine gas fuel lines. It is a one-way valve comprising a control ball, a valve chamber, an inlet pipe, an outlet pipe, a valve seat, and a ball seat. The valve chamber connects the inlet and outlet. Its main control component is the metal control ball installed within the valve chamber. The ball seat is installed in a recess within the valve chamber to accommodate the control ball. When fuel is delivered at a normal flow rate, it flows past one side of the control ball within the valve chamber, causing the control ball to suspend within the valve chamber due to the flow velocity. In a first embodiment, the valve seat is installed on the inner wall of the valve chamber where the inlet is located. A protrusion is provided inside the outlet pipe within the valve chamber to prevent the ball from obstructing the gas fuel. In the first embodiment, when the gaseous fuel delivery pipeline ruptures, the high-pressure gaseous fuel flowing back from the engine to the check valve presses the control ball onto the valve seat and seals it, thus closing the check valve. In the second embodiment, the valve seat is installed on the inner wall of the valve chamber at the outlet. When the gaseous fuel flow rate exceeds 1.5 times the normal value, the control ball will be pressed onto the valve seat and seal, thus closing the check valve. In this embodiment, the control ball only closes when the flow rate exceeds the normal value, and it does not mention that the control ball will automatically fall off at a certain compression ratio, thus failing to solve problems three and four. In this embodiment, the control ball can float freely and is suitable as a two-way valve for rapid filling applications, thus solving problem five.

[0040] Reference Case 8

[0041] US Patent 4120315A (1978) – Velocity check valve, a flow rate check valve for oil or gas wells, designed to prevent leakage and fire damage. It includes a control ball, a valve chamber, an inlet, an outlet, an annular seat, a push rod, and a ball seat. The valve chamber connects the inlet and outlet. Its main control component is the metal control ball housed within the valve chamber. The ball seat is installed in the valve chamber to accommodate the control ball. When fluid is flowing at a normal rate, the control ball is suspended in the valve chamber due to the flow rate. When the flow rate exceeds the limit, the control ball closes the flow rate check valve. At this point, the control ball establishes a pressure difference between the inlet and the outlet. When this pressure difference gradually decreases to near zero, the control ball will automatically drop. If the pressure difference remains unchanged, the control valve can be opened by using the handle push rod to push the control valve. In this reference design, the control ball only closes when the value exceeds the normal value. When the pressure difference of the control ball gradually decreases to near zero, the control ball will automatically drop, which cannot solve problems three and four. The control ball in this reference design can float freely and is suitable as a two-way valve for rapid filling applications, thus solving problem five.

[0042] When this micro-mechanism is introduced to solve problems one and two, the micro-mechanism itself needs to further overcome problems three, four, and five. Problem five seems easy to solve, but References four, five, and six do not offer good solutions for it. References one, two, three, four, five, six, seven, and eight do not provide good solutions for problems three and four. In other words, there are no good existing countermeasures for problems one through five. Only by further improving this micro-valve mechanism can it meet requirements one, two, three, and four, and achieve the unique requirements for transporting clean fluids and particulate suspended fluids. This invention will create a buffer valve, which is an innovative structure similar to a ball check valve in micro-mechanism, and will provide solutions to meet problems one through five, as well as requirements one through four. Summary of the Invention

[0043] The purpose of this invention is to provide a buffer valve.

[0044] To achieve the above objectives, the technical solution adopted by the present invention is as follows:

[0045] A micro-mechanism buffer valve is a bidirectional valve mounted on a pneumatic diaphragm valve. The pneumatic diaphragm valve includes a pneumatic cylinder, a diaphragm, and a valve seat. The pneumatic cylinder is divided into a pressure chamber and a spring chamber by a piston. The spring chamber is equipped with a spring. The spring chamber and the pressure chamber are each provided with a breather hole. The breather hole of the pressure chamber includes an inner chamber. The inner chamber is equipped with the buffer valve, and the buffer valve is equipped with a gas connector for filling with high-pressure gas. The buffer valve is used to adjust the flow rate of the breather hole and to adjust the release of high-pressure gas from the pressure chamber without affecting the filling speed of the high-pressure gas into the pressure chamber. A tool part is located on the outside of the buffer valve for installing or removing and installing the gas connector.

[0046] The diaphragm has an integral structure, comprising a circumferential portion, a central portion, and an elastic portion. The cross-sectional shape of the elastic portion resembles an Ω-shaped arc curve. Its characteristic is that:

[0047] During the process of a normally closed valve changing from an open state to a closed state and during the process of a normally open valve changing from a closed state to an open state, when high-pressure gas is released, the buffer valve can slow down the pressure shock wave generated by the release of high-pressure gas for a certain period of time. At the same time, the spring in the spring chamber is restricted when it extends and slowly releases its elastic force.

[0048] The central portion of the diaphragm in a normally closed valve reduces the approach velocity to the valve seat, thereby reducing the impact and decreasing the violent jetting generated by the valve seat when it is closed.

[0049] The reduced speed at which the diaphragm in the normally open valve moves away from the valve seat at the moment of departure can slow down the generation of local negative pressure and reduce the generation of intense eddies and turbulence.

[0050] The buffer valve has an internal flow channel comprising an inner micro-vent, an inner chamber, an outer vent, and a floating ball. The internal flow channel connects to the internal pressure chamber and also to the gas connector of an external high-pressure gas source. The inner chamber has a centerline, an inner annular surface, an inner end, and an outer end. The inner end connects to the pressure chamber through the inner micro-vent, which is positioned off-center from the centerline and close to the inner annular surface. The outer end of the inner chamber connects to the gas connector through the outer vent, which is positioned along the centerline of the inner chamber. The floating ball is housed within the inner chamber and floats with the high-pressure gas flow. The outer diameter d1 of the floating ball is smaller than the inner diameter D2 of the inner chamber. <D2;

[0051] The buffer valve has the following functions during operation, including a high filling action, a shielding action, a release action, a shielding time Δt, and an adjustment mechanism, wherein the release action includes a release mechanism.

[0052] The high-filling action means that when the pressure chamber is filled with high-pressure gas, the high-pressure gas will enter the inner chamber through the high-pressure pipeline and the outer air hole, and push the floating ball to the inner micro air hole without causing obstruction, thus maintaining the high-filling action of the high-pressure gas entering the pressure chamber.

[0053] The shielding action is as follows: when the pressure chamber releases high-pressure gas, the high-pressure gas enters the inner cavity through the inner micro-pore, and drives the floating ball to move towards the outer pore and shield the outer pore to slow down the release of high-pressure gas; the shielding action is caused by the floating ball and the inner diameter d3 opening of the outer pore forming a circular contact line C. The circular contact line C cannot achieve an airtight effect but only reduces the rate of gas leakage.

[0054] The shielding action is caused by a pressure difference Δ between the gas pressure and the pipeline pressure, which generates a clamping force Fp applied to the floating ball. The clamping force Fp is equal to the pressure difference Δ multiplied by the circular area of ​​the circular contact line C.

[0055] The release action refers to the process where, after the high-pressure gas is continuously released under the shielding action, the shielding action will be released by the release mechanism after the gas pressure decreases, causing the floating ball to shift and no longer shield, allowing the remaining high-pressure gas to be quickly discharged.

[0056] The release mechanism refers to a mechanism that uses one or more methods, such as the weight W of the floating ball, an elastic force Fs, and a magnetic force Fm, to resist the clamping force Fp and move the floating ball, thereby completing the release action.

[0057] The masking time Δt refers to the period from the generation of the masking action until the completion of the release action, which is called the masking time Δt.

[0058] The adjustment mechanism means that the length of the masking time Δt is adjusted through the release mechanism of the release action.

[0059] For the buffer valve of the micro mechanism described above, a conical angle 2θ is formed by connecting the center of the floating ball to the circular contact line C.

[0060] For the buffer valve of the micro mechanism described above, the circular contact line C is a narrow annular strip structure.

[0061] For the buffer valve of the micro mechanism described above, when the outer diameter d1 of the floating ball is smaller than the inner diameter d3 of the outer air hole, i.e., d1 < d3, the area of the circular contact line C is equal to the cross-sectional area of the outer diameter of the floating ball, and the annular area of the gap between the outer diameter d1 and the inner diameter d3 is not more than 50% of the cross-sectional area of the inner micro air hole to achieve slow air leakage.

[0062] For the buffer valve of the micro mechanism described above, the length of the masking time Δt of the masking action is proportional to the pressing force Fp; the length of the masking time Δt of the masking action is proportional to the size of the conical angle 2θ.

[0063] For the buffer valve of the micro mechanism described above, when the release mechanism uses the weight W of the machine, in the masking action, the weight W of the floating ball cannot resist the pressing force Fp, so the floating ball is fixed at the outer air hole. In the release mechanism, the pressing force Fp generated by the pressure difference ΔP cannot resist the weight W of the floating ball itself, causing the floating ball to displace into the inner cavity and no longer mask the outer air hole.

[0064] For the buffer valve of the micro mechanism described above, when the release mechanism uses the elastic force Fs of the machine, in the masking action, the elastic force Fs borne by the floating ball cannot resist the pressing force Fp, so the floating ball is fixed at the outer air hole. In the release mechanism, the pressing force Fp generated by the pressure difference ΔP cannot resist the elastic force Fs borne by the floating ball, causing the floating ball to displace into the inner cavity and no longer mask the outer air hole.

[0065] For the buffer valve of the micro mechanism described above, when the release mechanism uses the magnetic force Fm, in the masking action, the magnetic force Fm borne by the floating ball cannot resist the pressing force Fp, so the floating ball is fixed at the outer air hole. In the release mechanism, the pressing force Fp generated by the pressure difference ΔP cannot resist the magnetic force Fm borne by the floating ball, causing the floating ball to displace into the inner cavity and no longer mask the outer air hole.

[0066] The aforementioned micro-mechanism buffer valve, wherein the structure of the buffer valve includes: a micro-valve body, the breather hole, and the floating ball;

[0067] The micro-valve body is cylindrical in shape and includes an inner chamber, an outer chamber, an isolation section, and an external vent.

[0068] The vent includes an inner chamber and an inner micro-vent. The vent is mounted on the outer ring wall of the pressure chamber. The inner micro-vent is located in the inner chamber, offset from the axis of the inner chamber and close to the inner ring surface. The outer ring surface of the micro-valve body can couple and seal with the inner chamber of the vent. The outer chamber can be used to install the gas connector.

[0069] The isolation section is located in the middle of the micro-valve body and separates the inner chamber and the outer chamber located at both ends. The isolation section is provided with an external vent that connects the outer chamber and the inner chamber. The external vent is located on the axis.

[0070] The aforementioned micro-mechanism buffer valve, wherein the structure of the buffer valve includes: a micro-valve body, a breathing cap, and a floating ball;

[0071] The micro-valve body is cylindrical in shape and includes an inner chamber, an outer chamber, an isolation section, and an external vent.

[0072] The breathing cap is used to connect to the breathing hole and includes an inner chamber, an inner micro-vent, an external thread, etc.

[0073] The external threads of the breathing cap can couple and seal with the breathing hole;

[0074] The internal micro-pore is located on the breathing cover and is offset from the axis of the inner chamber but close to the inner annular surface, and can communicate with the breathing hole;

[0075] The outer circumferential surface of the micro-valve body is coupled and sealed to the inner chamber of the breathing cap;

[0076] The outer chamber can be used to install the gas connector;

[0077] The isolation section is located in the middle of the micro-valve body and separates the inner chamber and the outer chamber located at both ends. The isolation section is provided with an external vent that connects the outer chamber and the inner chamber. The external vent is located on the axis.

[0078] The buffer valve of the micro-mechanism, wherein the shielding action is such that the weight W of the floating ball cannot resist the clamping force Fp generated by the pressure difference ΔP, thus fixing the floating ball to the external air hole.

[0079] The buffer valve of the micro-mechanism, wherein the release mechanism is that the weight W of the floating ball itself exceeds the clamping force Fp generated by the pressure difference ΔP, causing the floating ball to shift into the inner chamber and no longer block the external vent.

[0080] The buffer valve of the micro-mechanism is wherein the release mechanism is reliably completed based on the ratio of the outer diameter d1 of the floating ball to the inner diameter D2 of the inner chamber, d1 / D2≦0.6.

[0081] The buffer valve of the micro-mechanism, wherein the outer diameter d1 of the floating ball is greater than the inner diameter d3 of the outer air hole, and the cone angle 2θ satisfies 10°≦θ≦60°.

[0082] The buffer valve of the micro-mechanism, wherein the adjustment mechanism is to adjust the weight W, outer diameter d1, and cone angle 2θ of the floating ball.

[0083] The aforementioned micro-mechanism buffer valve, wherein the structure of the buffer valve includes: a micro-valve body, the breather hole, the floating ball, a release mechanism, a retaining ring, and an adapter;

[0084] The micro-valve body is cylindrical in shape and includes an inner chamber, a connecting chamber, an isolation section and an external vent.

[0085] The breathing hole includes the inner chamber and the inner micro-air vent, and the breathing hole is installed on the outer ring wall of the pressure chamber;

[0086] The outer annular surface of the micro-valve body can couple and seal with the inner chamber of the breathing hole;

[0087] The internal micro-pores are located in the inner chamber at a position that is offset from the axis of the inner cavity and close to the inner annular surface;

[0088] The isolation section is installed between the inner chamber and the connecting chamber, and the isolation section is provided with an external vent that connects the connecting chamber and the inner chamber. The external vent is located on the axis line.

[0089] The inner diameter of the connecting chamber is larger than that of the inner cavity, which can airtightly fix the fixing ring and the adapter.

[0090] The adapter is installed at the open end of the connecting chamber and is located outside the fixing ring. The adapter is used to connect the gas connector to the high-pressure pipeline and connect to the pressure chamber.

[0091] The cylindrical retaining ring includes a shaft hole and one or more vent holes. The retaining ring can be installed and fixed at the bottom of the connecting chamber and pressed against the isolation part. The inner diameter of the shaft hole is smaller than the inner diameter of the outer vent hole and the vent hole can communicate with the outer vent hole.

[0092] The release mechanism comprises an adjusting shaft, a retaining ring, a set of retaining nuts, and a miniature spring.

[0093] The adjusting shaft includes an external thread, a ball seat, and a shaft. The disc-shaped ball seat is located at one end of the adjusting shaft and has an inwardly concave spherical surface, while the external thread is located at the other end of the adjusting shaft.

[0094] During assembly, the retaining ring is first fastened inside the connecting chamber, the adjusting shaft is first fitted onto the micro spring and its tail end is passed through the outer air hole and the shaft hole, leaving the ball seat on the inner chamber side, so that the micro spring can be fitted onto the adjusting shaft and pressed between the ball seat and the retaining ring; the inner diameter of the outer air hole is larger than the outer diameter of the ball seat, so that the adjusting shaft can move back and forth freely within the inner chamber and the outer air hole;

[0095] The shaft and the shaft hole are slidably fitted to support the adjusting shaft; the external thread of the adjusting shaft passing through the shaft hole will extend and be fitted with the fixing nut assembly to ensure that the adjusting shaft will not come loose from the position of the fixing ring when filled with high-pressure gas.

[0096] The aforementioned micro-mechanism buffer valve, wherein the structure of the buffer valve includes: a micro-valve body, a breather hole, a floating ball, a release mechanism, a retaining ring, a sliding sleeve, and an adapter.

[0097] The micro-valve body is cylindrical in shape and includes an inner chamber, a connecting chamber, an isolation section and an external vent.

[0098] The breathing hole includes the inner chamber and the inner micro-air vent, and the breathing hole is installed on the outer ring wall of the pressure chamber;

[0099] The outer annular surface of the micro-valve body can couple and seal with the inner chamber of the breathing hole;

[0100] The internal micro-pores are located in the inner chamber at a position that is offset from the axis of the inner cavity and close to the inner annular surface;

[0101] The isolation section is installed between the inner chamber and the connecting chamber, and the isolation section is provided with an external vent that connects the outer chamber and the connecting chamber. The external vent is located on the axis line.

[0102] The inner diameter of the connecting chamber is larger than that of the inner cavity, which can seal and fix the fixing ring and fix the airtight adapter;

[0103] The adapter is installed at the open end of the connecting chamber and is located outside the fixing ring. The adapter is used to connect the gas connector to the high-pressure pipeline and connect to the pressure chamber.

[0104] The cylindrical retaining ring includes one or more vent holes and a central screw hole. The retaining ring can be installed and fixed at the bottom of the connecting chamber and pressed against the isolation part. The inner diameter of the central screw hole is smaller than the inner diameter of the outer vent hole, and the vent hole can communicate with the outer vent hole.

[0105] The release mechanism has an adjusting shaft, a sliding sleeve, a retaining ring, a locking nut, a set of retaining nuts, and a miniature spring.

[0106] The adjusting shaft includes an external thread, a ball seat, and a shaft. The disc-shaped ball seat is located at one end of the adjusting shaft and has an inwardly concave spherical surface, while the external thread is located at the other end of the adjusting shaft.

[0107] The sleeve includes a sliding shaft hole, an adjusting plate and an external thread;

[0108] During assembly, the retaining ring is first fastened inside the connecting chamber. The external thread of the sliding sleeve is first fitted with the locking nut until the position of the adjusting plate, and then coupled with the central thread hole of the retaining ring. The adjusting shaft is first fitted with the miniature spring and its tail end is passed through the external air hole and the sliding shaft hole, leaving the ball seat on the side of the inner cavity. Moreover, the outer diameter of the external thread of the sliding sleeve is larger than the outer diameter of the miniature spring, so that the miniature spring can be fitted on the adjusting shaft and pressed between the ball seat and the sliding sleeve.

[0109] The inner diameter of the external vent is larger than the outer diameter of the ball seat, so that the adjusting shaft can move back and forth freely within the inner chamber and the external vent.

[0110] The shaft is slidably fitted with the sliding hole to support the adjusting shaft;

[0111] The adjusting disc of the sliding sleeve can be rotated to adjust its front and rear position and can be fixed with the locking nut. The position of the miniature spring will affect the position of the sliding sleeve and change the compression displacement ΔX.

[0112] The external thread of the adjusting shaft passing through the sliding shaft hole of the sliding sleeve will extend and be fitted with the fixing nut assembly to ensure that the adjusting shaft will not come loose from the position of the sliding sleeve when high-pressure gas is filled;

[0113] Adjusting the position of the sliding sleeve finely adjusts the compression displacement ΔX of the miniature spring, thereby changing the elastic force Fs. This can be achieved by fixing the elastic coefficient K of the miniature spring and the outer diameter d1 and weight W of the floating ball, thus changing the elastic force Fs and adjusting the duration Δt of the shielding time.

[0114] In the aforementioned micro-mechanism buffer valve, the shielding action is caused by high-pressure gas driving the floating ball to adhere tightly to the ball seat. The pressure difference ΔP generated by the high-pressure gas produces a clamping force Fp applied to the floating ball, which in turn clamps and pushes the micro spring through the ball seat, generating a compression displacement ΔX and an elastic force Fs. The compression displacement ΔX is the compression amount of the micro spring, and Fp ≧ Fs.

[0115] The buffer valve of the micro-mechanism, wherein the release mechanism is that the clamping force Fp generated by the pressure difference ΔP cannot resist the elastic force Fs of the micro-spring, and pushes the floating ball away and moves it into the inner cavity, no longer blocking the external air hole, Fp≦Fs.

[0116] The buffer valve of the micro-mechanism, wherein the release mechanism is not limited by the direction of the weight W of the floating ball and the direction of the clamping force F.

[0117] The buffer valve of the micro-mechanism, wherein the release mechanism is reliably completed based on the ratio of the outer diameter d1 of the floating ball to the inner diameter D2 of the inner chamber, d1 / D2≦0.8.

[0118] The buffer valve of the micro-mechanism, wherein the outer diameter d1 of the floating ball is greater than the inner diameter d2 of the outer air hole, and the cone angle 2θ satisfies 15°≦θ≦80°.

[0119] The buffer valve of the micro mechanism, wherein the adjustment mechanism, the shielding time Δt can be adjusted by the weight W of the floating ball, the outer diameter d1, and the elastic force Fs, etc., wherein the adjustment of the elastic force Fs refers to adjusting the elastic coefficient of the micro spring.

[0120] The buffer valve of the micro-mechanism, wherein the adjustment mechanism includes the fixing nut assembly, which can set the relative position of the ball seat of the adjustment shaft with respect to the opening of the external vent in the inner chamber, so as to ensure that the floating ball can reliably complete the shielding action and the release action.

[0121] The aforementioned micro-mechanism buffer valve, wherein the structure of the buffer valve includes: a micro-valve body, a breather cap, and a floating ball;

[0122] The micro-valve body is cylindrical in shape and includes an inner chamber, an outer chamber, an isolation section, an external vent, and a magnetic body; the outer chamber can be used to install the gas connector;

[0123] The breathing cap is used to connect the breathing hole and includes an inner chamber, an inner micro-vent, an external thread and a central post; the external thread of the breathing cap can be coupled and sealed with the breathing hole; the outer annular surface of the micro-valve body is coupled and sealed with the inner chamber of the breathing cap.

[0124] The central column of the breathing cap is installed at the center of the bottom of the inner chamber and is concentric with the axis, allowing it to extend into the inner chamber;

[0125] The internal micro-pore is offset from the axis of the internal chamber and is located at the inner end and close to the inner annular surface, and can communicate with the breathing hole;

[0126] The floating ball is cylindrical, with a spherical surface at its front end and a cylinder with a cylindrical blind hole at its rear end. A magnetic ring is installed inside the floating ball. The magnetic ring is in the shape of a long strip and is installed near the spherical surface. The axis line can extend through the center of the spherical surface, and the center of the magnetic ring is concentric with the center of the blind hole.

[0127] The isolation part is located in the middle of the micro-valve body and separates the inner cavity and the outer cavity at both ends, and is connected by the outer air hole, which is located on the axis line.

[0128] The magnetic body is annular and is installed on the side of the isolation part close to the inner cavity and is concentric with the outer air hole.

[0129] The floating ball is placed in the inner cavity and can move back and forth on the central column. A repulsive magnetic force Fm is generated between the magnetic ring of the floating ball and the magnetic body of the micro-valve body.

[0130] The shielding action is that the repulsive magnetic force Fm between the floating ball and the micro-valve body cannot resist the pressing force Fp generated by the pressure difference ΔP, Fm < Fp, so that the floating ball is fixed at the outer air hole.

[0131] The release mechanism is that the pressing force Fp generated by the pressure difference ΔP cannot resist the repulsive magnetic force Fm between the magnetic ring and the magnetic body, Fm > Fp, causing the floating ball to move backward to the inner cavity and no longer shield the outer air hole.

[0132] For the buffer valve of the micro mechanism described above, the release mechanism is not limited by the direction of the weight W of the floating ball and the direction of the pressing force F.

[0133] [[ID=2I]]For the buffer valve of the micro mechanism described above, the release action can be completed effectively due to the ratio of the outer diameter d1 of the floating ball to the inner diameter D2 of the inner cavity, d1 / D2 ≤ 0.9.

[0134] For the buffer valve of the micro mechanism described above, when the outer diameter d1 of the floating ball is larger than the inner diameter d2 of the outer air hole, the cone angle 2θ satisfies 10° ≤ θ ≤ 80°.

[0135] For the buffer valve of the micro mechanism described above, in the adjustment mechanism, the shielding time Δt can be adjusted by the outer diameter d1 and the magnetic force Fm. The adjustment mechanism of the magnetic force refers to adjusting the repulsive force between the magnetic ring and the magnetic body of the micro-valve body.

[0136] For the buffer valve of the micro mechanism described above, in the release mechanism, there is no directional limitation on the weight W, elastic force Fs, magnetic force Fm and pressing force Fp of the floating ball.

[0137] The aforementioned micro-mechanism buffer valve, wherein in a normally closed valve, when it is in an open state, it switches to a closed state, or in a normally open valve, when it is in a closed state, it switches to an open state; when high-pressure gas is released, the buffer valve can be activated immediately, the approach speed of the central portion of the diaphragm of the normally closed valve to the valve seat is immediately reduced, and the removal speed of the central portion of the diaphragm of the normally open valve from the valve seat is immediately reduced.

[0138] The aforementioned micro-mechanism buffer valve, wherein, during the process of the normally closed valve changing from an open state to a closed state and during the process of the normally open valve changing from a closed state to an open state, the certain time refers to the shielding time Δt of the buffer valve during the release of high-pressure gas, which continuously reduces the pressure shock wave generated by the release of high-pressure gas; in the normally closed valve, the approach speed of the central part of the diaphragm to the valve seat is reduced throughout the entire process, thereby reducing the impact and reducing the intense jet flow generated by the valve seat when it closes; in the normally open valve, the removal speed of the central part of the diaphragm from the valve seat is reduced throughout the entire process, which can slow down the generation of local negative pressure and reduce the generation of intense eddies and intense turbulence.

[0139] This invention provides a buffer valve for a miniature valve mechanism, which is a bidirectional valve. The buffer valve is mounted on a pneumatic diaphragm valve, which includes a pneumatic cylinder, a diaphragm, and a valve seat. The pneumatic cylinder is divided into a pressure chamber and a spring chamber by a piston. The spring chamber is equipped with a spring. Both the spring chamber and the pressure chamber have a breather hole. The buffer valve is installed in the breather hole of the pressure chamber, and the buffer valve is equipped with a gas connector for filling with high-pressure gas. The buffer valve is used to regulate the release of high-pressure gas from the pressure chamber without affecting the filling speed of the high-pressure gas into the pressure chamber. The buffer valve has a tool part located on the outside of the buffer valve for installing or removing the gas connector. The diaphragm is an integral structure consisting of a circumferential part, a central part, and an elastic part. The cross-sectional shape of the elastic part is similar to an Ω-shaped arc curve.

[0140] When high-pressure gas is released, the normally closed diaphragm valve can slow down the pressure shock wave generated by the release of high-pressure gas and the violent impact of the central part of the diaphragm on the valve seat for a certain period of time, reduce the approach speed of the central part to the valve seat and reduce the violent jet generated when the valve seat is closed.

[0141] When high-pressure gas is released, the normally open diaphragm valve can slow down the pressure shock wave generated by the release of high-pressure gas and the instantaneous movement speed of the central part away from the valve seat within a certain period of time. This can reduce the generation of local negative pressure and reduce the generation of intense eddies and turbulence.

[0142] Its patent features are:

[0143] The buffer valve has an internal flow channel comprising an inner micro-vent, an inner chamber, an outer vent, and a floating ball. This internal flow channel connects to the internal pressure chamber and also to the gas connector of an external high-pressure gas source. The elongated cylindrical inner chamber has a centerline, an inner annular surface, an inner end, and an outer end. The inner end connects to the pressure chamber via the inner micro-vent, which is positioned off-center from the centerline and close to the inner annular surface. The outer end of the inner chamber connects to the gas connector via the outer vent, which is positioned along the centerline of the inner chamber. The floating ball is housed within the inner chamber and floats with the high-pressure gas flow. The outer diameter d1 of the floating ball is smaller than the inner diameter D2 of the inner chamber. <D2。

[0144] The buffer valve has the following functions during operation, including a high filling action, a shielding action, a release action (including a release mechanism), a shielding time Δt, and an adjustment mechanism.

[0145] The high-filling action refers to the fact that when the pressure chamber is filled with high-pressure gas, the high-pressure gas will enter the inner chamber through the high-pressure pipeline and the outer air hole, and push the floating ball to the inner micro air hole without causing obstruction, thus maintaining the high-pressure gas entering the pressure chamber and having a high-filling action.

[0146] The shielding action occurs when high-pressure gas is released from the pressure chamber. The high-pressure gas enters the inner cavity through the internal micro-pore, causing the floating ball to move towards and shield the external pore, thus slowing down the release of the high-pressure gas. This shielding action is achieved by the floating ball and the inner diameter d3 opening of the external pore forming a circular contact line C. This circular contact line C does not achieve an airtight seal but only reduces the rate of gas leakage. The shielding action is caused by a pressure difference ΔP between the gas pressure and the pipeline pressure, generating a clamping force Fp applied to the floating ball. This clamping force Fp is equal to the pressure difference ΔP multiplied by the circular area of ​​the contact line C.

[0147] The release action refers to the process where, under the continuous release of high-pressure gas during the shielding action, the gas pressure decreases later, and the shielding action is released by the release mechanism to disengage the clamping force Fp, causing the floating ball to shift and no longer shield the external vent, allowing the remaining high-pressure gas to be quickly discharged. The release mechanism refers to a mechanism that uses one or more methods, such as the weight W of the floating ball, an elastic force Fs, and a magnetic force Fm, to resist the clamping force Fp and move the floating ball, thus completing the release action.

[0148] The masking time Δt refers to the period from the generation of the masking action until the completion of the release action, which is called the masking time Δt. During the process of a normally closed valve changing from an open state to a closed state and a normally open valve changing from a closed state to an open state, the certain time means that when high-pressure gas is released, the masking time Δt of the buffer valve slows down the pressure shock wave generated by the release of high-pressure gas throughout the process; the approaching speed of the central part of the diaphragm of the normally closed valve to the valve seat is reduced throughout the process to reduce impact, and the intense jet generated when the valve seat closes is reduced; the moving-away speed of the central part of the diaphragm of the normally open valve from the valve seat is reduced throughout the process, which can slow down the generation of local negative pressure and reduce the generation of intense eddy currents and turbulence.

[0149] The adjustment mechanism refers to the adjustment of the length of the masking time Δt through the weight W of the floating ball, an elastic force Fs, a magnetic force Fm, etc. of the release action.

[0150] Connect a straight line L1 from the circular contact line C to the center of the floating ball, and then from the center of the floating ball and the axis line of the inner diameter d3 of the outer air hole to form a straight line L2. The included angle θ formed by the straight line L1 and the straight line L2, that is, the cone angle 2θ formed by connecting from the center of the floating ball to the circular contact line C. The circular contact line C can also be a narrow annular band structure, for example, a chamfer is formed at the opening of the inner diameter d3 of the outer air hole. When the outer diameter d1 of the floating ball is smaller than the inner diameter d3 of the outer air hole, d1 < d3, the area of the circular contact line C is equal to the cross-sectional area of the outer diameter of the floating ball, and the annular area of the gap between the outer diameter d1 and the inner diameter d3 is not greater than 50% of the cross-sectional area of the inner micro air hole to achieve slow air release. The length of the masking time Δt of the masking action is proportional to the tightening force Fp; the length of the masking time Δt of the masking action is proportional to the size of the cone angle 2θ.

[0151] When the release mechanism uses the weight W of the floating ball, in the masking action, the weight W of the floating ball cannot resist the tightening force Fp, so the floating ball is fixed to the outer air hole. In the release mechanism, the tightening force Fp generated by the pressure difference ΔP cannot resist the weight W of the floating ball itself, causing the floating ball to displace into the inner cavity and no longer mask the outer air hole.

[0152] When the release mechanism uses the mechanical elastic force Fs, in the masking action, the elastic force Fs borne by the floating ball cannot resist the tightening force Fp, so the floating ball is fixed to the outer air hole. In the release mechanism, the tightening force Fp generated by the pressure difference ΔP cannot resist the elastic force Fs borne by the floating ball, causing the floating ball to displace into the inner cavity and no longer mask the outer air hole.

[0153] The release mechanism is that when the magnetic force Fm is applied, the shielding action is that the magnetic force Fm on the floating ball cannot resist the clamping force Fp, causing the floating ball to be fixed to the external air hole. The release mechanism is that the clamping force Fp generated by the pressure difference ΔP cannot resist the magnetic force Fm on the floating ball, causing the floating ball to shift to the inner cavity and no longer shield the external air hole.

[0154] First Embodiment

[0155] This embodiment further describes the invention. The structure of the buffer valve includes: a micro-valve body, a breather hole, and a floating ball; the micro-valve body is cylindrical in shape and includes an inner chamber, an outer chamber, an isolation part, and an external vent; the outer chamber can be used to install the gas connector; the breather hole includes an inner chamber and an inner micro-vent, the breather hole is installed on the outer ring wall of the pressure chamber, and the inner micro-vent is located in the inner chamber at a position away from the axis of the inner chamber and close to the inner ring surface; the outer ring surface of the micro-valve body is coupled and sealed with the inner chamber of the breather hole; the isolation part is located in the middle of the micro-valve body and separates the inner chamber and the outer chamber located at two ends, and the isolation part is provided with an external vent that connects the outer chamber and the inner chamber, and the external vent is located on the axis.

[0156] Second Embodiment

[0157] This embodiment further describes the invention. The structure of the buffer valve includes: a micro-valve body, a breathing cap, and a floating ball; the micro-valve body is cylindrical in shape and includes an inner chamber, an outer chamber, an isolation portion, and an external vent; the breathing cap is used to connect to the breathing hole and includes an inner chamber, an inner micro-vent, and an external thread; the external thread of the breathing cap can be coupled and sealed with the breathing hole; the inner micro-vent is located on the breathing cap and is offset from the axis of the inner chamber but close to the inner annular surface, and can communicate with the breathing hole; the outer annular surface of the micro-valve body is coupled and sealed with the inner chamber of the breathing cap; the outer chamber can be used to install the gas connector; the isolation portion is located in the middle of the micro-valve body and separates the inner chamber and the outer chamber located at both ends, and the isolation portion is provided with an external vent that connects the outer chamber and the inner chamber, and the external vent is located on the axis.

[0158] As described in the first and second embodiments, the shielding action occurs when the weight W of the floating ball cannot resist the clamping force Fp generated by the pressure difference ΔP, thus fixing the floating ball to the external vent. As described in the first and second embodiments, the release action and release mechanism occur when the weight W of the floating ball itself exceeds the clamping force Fp generated by the pressure difference ΔP, causing the floating ball to shift into the inner chamber and no longer shield the external vent.

[0159] As described in the first and second embodiments, the release action is reliably completed based on the ratio of the outer diameter d1 of the floating ball to the inner diameter D2 of the inner cavity, where d1 / D2 ≤ 0.6. As described in the first and second embodiments, the outer diameter d1 of the floating ball is greater than the inner diameter d3 of the external vent, and the cone angle is 2θ, where 10° ≤ θ ≤ 60°.

[0160] As described in the first and second embodiments, the adjustment mechanism involves adjusting parameters such as the weight W, outer diameter d1, and cone angle 2θ of the floating ball.

[0161] Third Embodiment

[0162] This embodiment further describes the invention. The buffer valve structure includes: a micro-valve body, a breather hole, a floating ball, a release mechanism, a fixing ring, and an adapter. The micro-valve body is cylindrical and includes an inner chamber, a connecting chamber, an isolation portion, and an external vent. The breather hole includes an inner chamber and an internal micro-vent, and is installed on the outer ring wall of the pressure chamber. The outer ring surface of the micro-valve body is coupled and sealed to the inner chamber of the breather hole. The internal micro-vent is located in the inner chamber, offset from the axis of the inner chamber and close to the inner ring surface. The isolation portion is installed between the inner chamber and the connecting chamber. Between the connecting chambers, the isolation part is provided with an external vent that connects the connecting chamber and the inner chamber, and the external vent is located on the axis line; the inner diameter of the connecting chamber is larger than that of the inner chamber, so that the fixing ring and the adapter can be airtightly fixed; the adapter is installed at the open end of the connecting chamber and is located outside the fixing ring, and the adapter is used to connect the gas connector and the high-pressure pipeline and connect to the pressure chamber; the cylindrical fixing ring includes a shaft hole and one or more vent holes, and can be installed and fixed at the bottom of the connecting chamber and pressed against the isolation part, the inner diameter of the shaft hole is smaller than the inner diameter of the external vent hole, and the vent hole can communicate with the external vent hole. The release mechanism includes an adjusting shaft, a retaining ring, a set of retaining nuts, and a miniature spring. The adjusting shaft includes an external thread, a ball seat, and a shaft. The disc-shaped ball seat has a concave spherical surface at one end of the adjusting shaft, and the external thread is located at the other end. During assembly, the retaining ring is first fastened to the interior of the connecting chamber. The adjusting shaft is first fitted with the miniature spring, and its tail end passes through the external vent and the shaft hole, leaving the ball seat on the inner chamber side. This allows the miniature spring to be fitted onto the adjusting shaft and pressed between the ball seat and the retaining ring. The inner diameter of the external vent is larger than the outer diameter of the ball seat, allowing the adjusting shaft to move freely back and forth within the inner chamber and the external vent. The shaft slides into the shaft hole to support the adjusting shaft. The external thread of the adjusting shaft, passing through the shaft hole, extends and is fitted with the set of retaining nuts, ensuring that the adjusting shaft will not loosen from the retaining ring when filled with high-pressure gas.

[0163] Fourth embodiment

[0164] This embodiment further describes the invention. The structure of the buffer valve includes: a micro-valve body, a breather hole, a floating ball, a release mechanism, a fixing ring, a sliding sleeve, and an adapter. The micro-valve body is cylindrical and includes an inner chamber, a connecting chamber, an isolation portion, and an external vent. The breather hole includes an inner chamber and an inner micro-vent, and is installed on the outer ring wall of the pressure chamber. The outer ring surface of the micro-valve body is coupled and sealed to the inner chamber of the breather hole. The inner micro-vent is located in the inner chamber, offset from the axis of the inner chamber and close to the inner ring surface. The isolation portion is installed between the inner chamber and the connecting chamber, and the isolation portion has an external vent connecting the outer chamber and the connecting chamber. The inner diameter of the chamber is larger than the inner cavity, which can seal and fix the fixing ring and the airtight adapter; the adapter is installed at the open end of the connecting chamber and is located outside the fixing ring. The adapter is used to connect the gas connector and the high-pressure pipeline and connect to the pressure chamber; the cylindrical fixing ring includes one or more vent holes and a central screw hole, which can be installed and fixed at the bottom of the connecting chamber and pressed against the isolation part. The inner diameter of the central screw hole is smaller than the inner diameter of the outer vent hole and can communicate with the outer vent hole; the structure of the release mechanism includes an adjusting shaft, the sliding sleeve, the fixing ring, a locking nut, a fixing nut assembly and a miniature spring, etc.; the adjusting shaft includes an external thread, a ball seat, a shaft, etc., and the disc-shaped ball seat is located on the adjusting shaft. The end has a concave spherical surface, and the external thread is located at the other end of the adjusting shaft. The sliding sleeve includes a sliding shaft hole, an adjusting plate, and an external thread. During assembly, the retaining ring is first fastened to the interior of the connecting chamber. The external thread of the sliding sleeve is first fitted with the locking nut until the position of the adjusting plate, and then coupled with the central thread hole of the retaining ring. The adjusting shaft is first fitted with the miniature spring and its tail end passes through the external vent and the sliding shaft hole, leaving the ball seat on the side of the inner cavity. Moreover, the outer diameter of the external thread of the sliding sleeve is larger than the outer diameter of the miniature spring, so that the miniature spring can be fitted on the adjusting shaft and pressed between the ball seat and the sliding sleeve. The inner diameter of the external vent is larger than the outer diameter of the ball seat, so that the adjusting shaft can move back and forth freely within the inner cavity and the external vent. The shaft and the sliding hole slide together to support the adjusting shaft; the adjusting disc of the sliding sleeve can be rotated to adjust its front and rear positions and can be fixed with the locking nut; the position of the miniature spring will affect the position of the sliding sleeve and change the compression displacement ΔX; the external thread of the adjusting shaft passing through the sliding hole of the sliding sleeve will extend and be fitted with the fixing nut assembly to ensure that the adjusting shaft will not come loose from the position of the sliding sleeve when filled with high-pressure gas; adjusting the position of the sliding sleeve can finely adjust the compression displacement ΔX of the miniature spring to change the elastic force Fs. With the elastic coefficient K of the miniature spring fixed and the outer diameter d1 and weight W of the floating ball fixed, the elastic force Fs can be changed so that the shielding time Δt can be adjusted.

[0165] As described in the third and fourth embodiments, the shielding action is caused by high-pressure gas driving the floating ball to adhere tightly to the ball seat. The pressure difference ΔP generated by the high-pressure gas produces a clamping force Fp applied to the floating ball, which in turn clamps the micro-spring via the ball seat, generating a compression displacement ΔX and a spring force Fs. The compression displacement ΔX is the compression amount of the micro-spring, and Fp ≥ Fs. As described in the third and fourth embodiments, the release action and release mechanism are such that the clamping force Fp generated by the pressure difference ΔP cannot resist the spring force Fs of the micro-spring, thus pushing the floating ball away and moving it into the inner cavity, no longer shielding the external air hole, and Fp ≤ Fs.

[0166] As described in the third and fourth embodiments, the release mechanism is not limited by the direction of the weight W of the floating ball and the direction of the clamping force F.

[0167] As described in the third and fourth embodiments, the release action is reliably completed based on the ratio of the outer diameter d1 of the floating ball to the inner diameter D2 of the inner cavity, where d1 / D2 ≤ 0.8. As described in the third and fourth embodiments, the outer diameter d1 of the floating ball is greater than the inner diameter d3 of the external vent, and the cone angle is 2θ, where 15° ≤ θ ≤ 80°.

[0168] As described in the third and fourth embodiments, the shielding time Δt of the adjustment mechanism can be adjusted by the weight W, outer diameter d1, and elastic force Fs of the floating ball, wherein adjusting the elastic force Fs refers to adjusting the elastic coefficient of the miniature spring. As described in the third and fourth embodiments, the adjustment mechanism includes a fixing nut assembly, which can set the relative position of the ball seat to the external vent in the inner cavity side opening, ensuring that the floating ball can reliably complete the shielding and releasing actions.

[0169] Fifth Embodiment

[0170] This embodiment is further described according to the invention content. The structure of the buffer valve includes: a micro-valve body, a breathing cover, a floating ball, etc.; the floating ball is cylindrical, with a spherical surface at its front end and a cylinder with a cylindrical blind hole at its rear end. A magnetic ring is installed inside the floating ball. The magnetic ring is in the shape of a long strip and is installed near the spherical surface, and its annular center is concentric with the blind hole; the outer shape of the micro-valve body is cylindrical and consists of the inner cavity, an outer cavity, a partition, the outer air hole, a magnetic body, etc.; the outer cavity can be used to install the gas connector; the partition is located in the middle of the micro-valve body and separates the inner cavity and the outer cavity at both ends, and is connected to each other by the outer air hole. The outer air hole is installed at the center of the partition; the magnetic body is annular and is installed on the side of the partition near the inner cavity and is concentric with the outer air hole; the breathing cover is used to connect the breathing hole and includes an inner cavity, the inner micro-air hole, an external thread, a central column, etc.; the external thread of the breathing cover can be coupled and sealed with the breathing hole; the inner micro-air hole is located on the breathing cover and is offset from the axis of the inner cavity and is close to the inner ring surface and can communicate with the breathing hole; the central column of the breathing cover is installed at the center of the bottom of the inner cavity, can extend into the inner cavity and can be inserted into the blind hole of the floating ball; the outer ring surface of the micro-valve body is coupled and sealed with the inner cavity of the breathing cover; the floating ball is placed in the internal flow channel and can move back and forth on the central column.

[0171] A mutually repulsive magnetic force Fm is generated between the magnetic ring of the floating ball and the magnetic body of the micro-valve body; the shielding action is that the mutually repulsive magnetic force Fm of the floating ball and the micro-valve body cannot resist the pressing force Fp generated by the pressure difference ΔP, Fm < Fp, and the floating ball is fixed to the outer air hole; the release mechanism is that the pressing force Fp generated by the pressure difference ΔP cannot resist the mutually repulsive magnetic force Fm of the magnetic ring and the magnetic body, Fm > Fp, causing the floating ball to move backward to the inner cavity and no longer shield the outer air hole. As described in the fifth embodiment, the release mechanism is not limited by the direction of the weight W of the floating ball and the direction of the pressing force F.

[0172] As described in the fifth embodiment, the release action can be completed reliably due to the ratio of the outer diameter d1 of the floating ball to the inner diameter D2 of the inner cavity, d1 / D2 ≦ 0.8; as described in the fifth embodiment, when the outer diameter d1 of the floating ball is greater than the inner diameter d3 of the outer air hole, the cone angle 2θ, 15° ≦ θ ≦ 80°.

[0173] As described in the fifth embodiment, for the adjustment mechanism, the shielding time Δt can be adjusted by the weight W, outer diameter d1 of the floating ball, and the magnetic force Fm, etc. The adjustment mechanism of the magnetic force refers to adjusting the mutually repulsive force between the magnetic ring and the magnetic body of the micro-valve body.

[0174] The above-described contents and embodiments of the present invention can solve problems 1, 2, 3, 4 and 5, and fully satisfy requirements 1, 2, 3 and 4, achieving the unique requirements for the transportation of clean fluids and particulate suspension fluids. The contents of the present invention will be further described below with several embodiments. Attached Figure Description

[0175] Figure 1 This is a cross-sectional view of the pneumatic diaphragm valve.

[0176] Figure 2 This is a cross-sectional view of the vent.

[0177] Figure 3A This is a diagram showing the positions of the floating ball and the internal micro-pores when the air chamber is inflated.

[0178] Figure 3B This is a diagram showing the composition of the floating ball, the external vent, and the cone angle 2θ during the initial stage of high-pressure gas release.

[0179] Figure 3C yes Figure 3B Enlarged image.

[0180] Figure 3D This is a diagram showing the position of the floating ball relative to the inner chamber at the end of the high-pressure gas release phase.

[0181] Figure 4 This is a cross-sectional view of the buffer valve 2a in the first embodiment.

[0182] Figure 5 This is a cross-sectional view of the buffer valve 2b in the second embodiment.

[0183] Figure 6A This is a cross-sectional view of the buffer valve 2c in the third embodiment, especially its micro-valve body 21c structure.

[0184] Figure 6B This is a diagram showing the configuration of the floating ball, the external vent, and the cone angle 2θ of the buffer valve 2c in the initial stage of high-pressure gas release in the third embodiment.

[0185] Figure 6C yes Figure 6B Enlarged image.

[0186] Figure 6D The third embodiment shows the position of the floating ball and the inner chamber of the buffer valve 2c at the end of the high-pressure gas release.

[0187] Figure 6E yes Figure 6D Enlarged image.

[0188] Figure 7A This is a 2d cross-sectional view of the fourth implementation of the buffer valve, particularly its micro-valve body 21d structure.

[0189] Figure 7B This is a diagram illustrating the configuration of the floating ball, the external vent, and the cone angle 2θ of the buffer valve 2d in the initial stage of high-pressure gas release, according to the fourth embodiment.

[0190] Figure 7C yes Figure 7B Enlarged image.

[0191] Figure 7D The fourth embodiment shows the position diagram of the floating ball and the inner chamber at the end of the high-pressure gas release period of the buffer valve 2d.

[0192] Figure 7E yes Figure 7D Enlarged image.

[0193] Figure 8A This is a cross-sectional view of the buffer valve 2e in the fifth embodiment.

[0194] Figure 8B This is a cross-sectional view of the micro-valve body 21e in the fifth embodiment.

[0195] Figure 8C This is a diagram showing the configuration of the floating ball, the external vent, and the cone angle 2θ of the buffer valve 2e in the initial stage of high-pressure gas release in the fifth embodiment.

[0196] Figure 8D yes Figure 8C Enlarged image.

[0197] Figure 8E The fifth embodiment shows the position diagram of the floating ball and the inner chamber at the end of the high-pressure gas release period of the buffer valve 2e.

[0198] Figure 8F yes Figure 8E Enlarged image.

[0199] Reference numerals: 1-Pneumatic diaphragm valve; 10-Pneumatic cylinder; 11-Diaphragm; 111-Circumferential part; 112-Central part; 113-Elastic part; 114-Arc-shaped curve; 115-Approach speed; 116-Removal speed; 12-Valve seat; 13-Piston; 14-Pneumatic chamber; 141-Breath port; 142-Airflow; 143-Inner chamber; 15-Spring chamber; 151-Spring; 152-Breath port; 16-Gas connector; 161-High-pressure pipeline 2 / 2a / 2b / 2c / 2d / 2 e-Buffer valve; 213-Isolation section; 22-Internal flow channel; 221-Internal micro-pores; 222-Inner chamber; 223-Centerline; 224-Inner annular surface; 225-Inner end; 226-Outer end; 227-External pore; 23 / 23a-Floating ball; 236-High filling action; 230-Shielding action; 231-Release action; 24 / 24a / 24b / 24c / 24d-Release mechanism; 28-Adjustment mechanism; Δt-Shielding time; d1-Outer diameter of floating ball; D2-Inner diameter of inner chamber ; d3 - Inner diameter of external vent; C - Circular contact line; L1 - Straight line; L2 - Straight line; θ - Angle; 2θ - Cone angle; ΔP - Pressure difference; Fp - Compressive force; W - Weight; Fs - Elastic force; Fm - Magnetic force; ΔX - Compression displacement; 21a / 21b / 21c / 21d / 21e - Micro-valve body; 212 - Outer chamber; 213 - Isolation section; 215 - External thread; 216 - Internal thread; 20a / 20b - Breathing cover; 202 - Inner chamber; 203 - External thread; 218 - Connecting chamber; 25a / 25b-Fixing ring; 251-Shaft hole; 252-Outer ring surface; 253-Ventilation hole; 254-Center threaded hole; 240-Adjusting shaft; 241-External thread; 242-Spherical seat; 243-Shaft; 244-Fixing nut assembly; 245-Miniature spring; 26-Sliding sleeve; 261-Sliding shaft hole; 262-Adjusting disc; 263-External thread; 264-Locking nut; 219-Magnetic body; 204-Center column; 232-Spherical curved surface; 233-Cylinder; 234-Blind hole; 235-Magnetic ring. Detailed Implementation

[0200] Please refer to the accompanying diagrams for all instructions. Figure 1 , Figure 2 , Figure 3A , Figure 3B , Figure 3C , Figure 3D , Figure 4 , Figure 5 , Figure 6A , Figure 6B , Figure 6C , Figure 6D , Figure 6E , Figure 7A , Figure 7B , Figure 7C , Figure 7D , Figure 7E , Figure 8A , Figure 8B , Figure 8C , Figure 8D , Figure 8E , Figure 8F .

[0201] Please refer to Figure 1 and Figure 2 The following schematic diagrams all use normally closed valves as examples. Applications of normally open valves are supplemented with textual descriptions. This invention is a buffer valve 2, a bidirectional valve. This buffer valve 2 is installed on a pneumatic diaphragm valve 1 to regulate the release of its high-pressure gas without affecting its high-pressure gas filling action 236 (high-pressure gas filling action 236 is as follows). Figure 3A The pneumatic diaphragm valve 1 includes a pneumatic cylinder 10, a diaphragm 11, a valve seat 12, etc. The pneumatic cylinder 10 is divided into a pressure chamber 14 and a spring chamber 15 by a piston 13. The spring chamber 15 is equipped with a spring 151 and has a breather hole 152. The pressure chamber 14 has a breather hole 141. The existing diaphragm 11 is an integral structure with a circumferential part 111, a central part 112 and an elastic part 113. The cross-sectional shape of the elastic part 113 is similar to an Ω-shaped arc curve 114. The buffer valve 2 is installed in the breather hole 141 of the pressure chamber 14 to adjust the flow rate of the breather hole 141.

[0202] in:

[0203] When high-pressure gas is released, the buffer valve 2 of the normally closed pneumatic diaphragm valve 1 can reduce the pressure shock wave generated by the release of high-pressure gas and the violent impact of the central part 112 on the valve seat 12 for a certain period of time. When high-pressure gas is released, the buffer valve 2 of the normally open pneumatic diaphragm valve (not shown) can reduce the pressure shock wave generated by the release of high-pressure gas and the instantaneous retraction speed of the central part 112 away from the valve seat 12 for a certain period of time, thereby reducing the generation of local negative pressure and reducing the generation of violent eddies and turbulence. Preferably, when high-pressure gas is released, the buffer valve 2 can be activated immediately and operate throughout the entire process. The approach speed of the central part 112 of the diaphragm 11 of the normally closed valve to the valve seat 12 is reduced throughout the entire process, thereby reducing the impact. The retraction speed of the central part 112 of the diaphragm 11 of the normally open valve away from the valve seat 12 is reduced throughout the entire process, thereby reducing the generation of local negative pressure.

[0204] A gas connector 16 is installed on the buffer valve 2, which can be connected to a high-pressure pipeline 161. The buffer valve 2 has a tool part 217 on the outside, which is used to install or remove the buffer valve 2 and the gas connector 16.

[0205] Please refer to Figure 2The internal flow channel 22 of the buffer valve 2 includes an internal micro-air hole 221, an internal chamber 222, an external air hole 227, a floating ball 23, etc. The internal flow channel 22 can be connected to the internal pressure chamber 14 and also to the gas connector 16 of the external high-pressure gas source.

[0206] The elongated cylindrical inner chamber 222 has a centerline 223, an inner annular surface 224, an inner end 225, and an outer end 226. An internal micro-vent 221 is installed at the inner end 225, communicating with the pressure chamber 14. The internal micro-vent 221 is positioned off the centerline 223 and close to the inner annular surface 224. An external vent 227 is installed at the outer end 226 and located on the centerline 223. The external vent 227 communicates with the gas connector 16 and is positioned on the centerline 223. A floating ball 23 is placed inside the inner chamber 222 and floats with the high-pressure airflow. The outer diameter d1 of the floating ball 23 is smaller than the inner diameter D2 of the inner chamber. <D2。

[0207] The buffer valve 2 has the following functions during operation, including a high filling action 236, a shielding action 230, a release action 231, a shielding time Δt, an adjustment mechanism 28, and a release mechanism 24.

[0208] Please refer to Figure 3A The high filling action 236 refers to the fact that when the pressure chamber 14 is filled with high-pressure gas, the airflow 142 of the high-pressure gas will enter the internal flow channel 22 through the gas connector 16 and the external air hole 227, and push the floating ball 23 to the inner end 225 of the inner cavity 222 without blocking the internal micro air hole 221, thus maintaining the high filling action 236 of the high-pressure gas entering the pressure chamber 14 through the internal micro air hole 221.

[0209] Please refer to Figure 3B and Figure 3C The shielding action 230 occurs when the pressure chamber 14 releases high-pressure gas. The high-pressure gas enters the internal flow channel 22 through the inner micro-pore 221 and drives the floating ball 23 to move towards the outer pore 227, thus generating the shielding action 230 to slow down the release of high-pressure gas flow. The shielding action 230 is caused by the floating ball 23 and the inner diameter d3 opening of the outer pore 227 forming a circular contact line C without a sealing surface. The circular contact line C cannot achieve an airtight effect but only reduces the speed of gas leakage.

[0210] Please refer to Figure 3C, a straight line L1 is formed by connecting the center of the floating ball 23 with the circular contact line C, and then a straight line L2 is formed by connecting the center of the floating ball 23 with the center of the inner diameter d3 of the outer air hole 227. The straight line L2 is approximately concentric with the axis line 223. Then, an included angle θ is formed between the straight line L1 and the straight line L2. That is, a conical angle 2θ is formed by connecting the center of the floating ball 23 to the circular contact line C, which is twice the included angle θ. The shielding action 230 is caused by a pressure difference ΔP between the gas pressure and the pipeline pressure generating a tightening force Fp applied to the floating ball 23. The tightening force Fp is equal to the pressure difference ΔP multiplied by the circular area of the circular contact line C. The circular contact line C can also be a narrow annular strip structure without airtight function, and the annular strip structure forms a chamfer at the opening of the inner diameter d3 of the outer air hole 227, for example. When the outer diameter d1 of the floating ball 23 is smaller than the inner diameter d3 of the outer air hole 227, i.e., d1 < d3, the area of the circular contact line C is equal to the cross-sectional area of the outer diameter of the floating ball 23. At this time, the annular area of the unilateral gap is not greater than 50% of the cross-sectional area of the inner micro air hole 221 to achieve slow air leakage.

[0211] Please refer to Figure 3C and Figure 3D , the release action 231 means that under the shielding action 230, when the high-pressure gas is continuously released and later the gas pressure decreases and the pressure difference ΔP with the pipeline pressure decreases, the shielding action 230 will be replaced by the release action 231, allowing the remaining high-pressure gas to be quickly discharged. The release action 231 is to release the tightening force Fp through the release mechanism 24, causing the floating ball 23 to displace and no longer shield, so that the remaining high-pressure gas can be quickly released.

[0212] The release mechanism 24 refers to a mechanism that uses one or more of the weight W of the floating ball, an elastic force Fs, a magnetic force Fm, etc. to resist the tightening force Fp or move the floating ball 23 to complete the release action 231.

[0213] The shielding time Δt refers to the period from the generation of the shielding action 230 until the completion of the release action 231, which is called the shielding time Δt.

[0214] The adjustment mechanism 28 refers to adjusting the length of the shielding time Δt through the weight W of the floating ball 23, an elastic force Fs, a magnetic force Fm, etc. of the release action 231.

[0215] The length of the shielding time Δt of the shielding action 230 is proportional to the tightening force Fp; the length of the shielding time Δt of the shielding action 230 is proportional to the size of the conical angle 2θ.

[0216] The release mechanism 24 is called the release mechanism 24a when the weight W of the floating ball 23 is used. The shielding action 230 is when the weight W of the floating ball 23 cannot resist the clamping force Fp, causing the floating ball 23 to be fixed to the external vent 227. The release mechanism is when the clamping force Fp generated by the pressure difference ΔP cannot resist the weight W of the floating ball 23 itself, causing the floating ball 23 to shift to the inner cavity 222 and no longer shield the external vent 227.

[0217] When the release mechanism 24 utilizes the mechanical elastic force Fs, it is called the release mechanism 24b / 24c. The shielding action 230 is that the elastic force Fs borne by the floating ball 23 cannot resist the clamping force Fp, causing the floating ball 23 to be fixed to the external vent 227. The release mechanism is that the clamping force Fp generated by the pressure difference ΔP cannot resist the elastic force Fs borne by the floating ball 23, causing the floating ball 23 to shift to the inner cavity 222 and no longer shield the external vent 227.

[0218] The release mechanism 24 is called the release mechanism 24d when the magnetic force Fm is used. The shielding action 230 is that the magnetic force Fm on the floating ball 23 cannot resist the clamping force Fp, so the floating ball 23 is fixed to the external air hole 227. The release mechanism 24 is that the clamping force Fp generated by the pressure difference ΔP cannot resist the magnetic force Fm on the floating ball 23, so the floating ball 23 is displaced to the inner cavity 222 and no longer shields the external air hole 227.

[0219] When high-pressure gas is filled at high speed in normally open and normally closed valves, the spring 151 in the spring chamber 15 will have a higher rebound force as it is compressed more. This rebound force can provide a good buffering effect and will not cause too much impact. The pressure chamber 14 bears the gradually increasing pressure, which reduces the vibration of the high-pressure gas.

[0220] Please refer to Figure 1 For normally closed valves, this will slow down the approach velocity 115 of the central part 112 and reduce the impact on the valve seat 12, reduce the jetting caused by water hammer effect, reduce the pressure wave transmission along the upstream and downstream of the pipeline, extend the service life of equipment or joints and improve reliability, and prevent excessive particles from being released and contaminating clean liquids.

[0221] Please refer to Figure 1 For normally open valves, this will reduce the opening speed of the central part by 116, thus reducing the generation of a brief negative pressure vacuum and also reducing the generation of brief, intense turbulence and eddies in the fluid.

[0222] First Embodiment

[0223] Please refer to Figure 4The structure of the buffer valve 2a includes: a micro-valve body 21a, a breather hole 141, and a floating ball 23 (the release mechanism 24a); the breather hole 141 includes an inner chamber 143 and an inner micro-vent 221; the micro-valve body 21a is cylindrical in shape and includes an inner chamber 222, an outer vent 227, an outer chamber 212, an isolation portion 213, an internal thread 216, and an external thread 215; the breather hole 141 is installed on the outer ring wall of the pressure chamber 14, and the inner micro-vent 221 is located in the inner chamber 143 at a position away from the axis 223 of the inner chamber 222 and close to the inner ring surface 224, which can connect to the interior of the pressure chamber 14; the inner chamber 143 has an internal thread. 215; The floating ball 23 is installed in the inner chamber 222; The long cylindrical inner chamber 222 has the axis 223, the inner annular surface 224, the inner end 225 and the outer end 226; The isolation part 213 is located in the middle of the micro-valve body 21a and separates the inner chamber 222 and the outer chamber 212 located at both ends; The external vent 227 is installed on the isolation part 213 and is located on the axis 223, and the external vent 227 connects the inner chamber 222 and the outer chamber 212; The outer annular surface of the inner chamber 222 is provided with the external thread 215, which can couple and seal with the internal thread of the inner chamber 143 of the breathing hole 14; The outer chamber 212 has the internal thread 216 for installing the gas connector 16.

[0224] Second Embodiment

[0225] Please refer to Figure 5The buffer valve 2b is further evolved into an independent device. The structure of the buffer valve 2b includes: a micro-valve body 21b, a breathing cap 20a, and a floating ball 23 (the release mechanism 24a); the breathing cap 20a includes an inner chamber 202, an inner micro-vent 221, and an external thread 203; the breathing cap 20a is used to connect to the breathing hole 141 of the pressure chamber 14. The inner micro-vent 221 is offset at the bottom of the inner chamber 202 away from the center and communicates with the breathing hole 141. The inner chamber 202 has an internal thread that couples and seals with the micro-valve body 21b; the micro-valve body 21b is cylindrical in shape and includes the inner chamber 222, the external vent 227, an outer chamber 212, an isolation portion 213, and an external thread. The inner chamber 222 is composed of a 215 and an internal thread 216; the floating ball 23 is installed in the inner chamber 222; the long cylindrical inner chamber 222 has the axis 223, the inner ring surface 224, the inner end 225 and the outer end 226; the outer ring surface of the inner chamber 222 is provided with the external thread 215, which can couple and seal with the internal thread of the inner chamber 202 of the breathing cover 20a; the isolation part 213 is located in the middle of the micro-valve body 21b and separates the inner chamber 222 and the outer chamber 212 located at the two ends; the external vent 227 is installed in the isolation part 213 and is located on the axis 223, and the external vent 227 connects the inner chamber 222 and the outer chamber 212; the outer chamber 212 has the internal thread 216 for installing the gas connector 16.

[0226] As in the first embodiment and the second embodiment Figure 4 and Figure 5 As stated above, please refer to the following: Figure 3B , Figure 3C , Figure 3D The shielding action 230 occurs when the weight W of the floating ball 23 cannot resist the clamping force Fp generated by the pressure difference ΔP, thus fixing the floating ball 23 to the external vent 227. When the outer diameter d1 of the floating ball 23 is greater than the inner diameter d3 of the external vent 227, the cone angle 2θ is 10°≦θ≦60°. The release action 231 and the release mechanism 24a occur when the weight W of the floating ball 23 itself exceeds the clamping force generated by the pressure difference ΔP. Fp causes the floating ball 23 to shift into the inner cavity 222 and no longer block the outer vent 227; the release action 231 can be reliably completed by the ratio of the outer diameter d1 of the floating ball 23 to the inner diameter D2 of the inner cavity 222, d1 / D2≦0.6; the adjustment mechanism 28 adjusts the weight W, outer diameter d1 and cone angle 2θ of the floating ball 23, etc., the cone angle 2θ, 10°≦θ≦60°.

[0227] Third Embodiment

[0228] Please refer to Figure 6A , Figure 6B , Figure 6C , Figure 6D and Figure 6E, the structure of the buffer valve 2c includes: a micro valve body 21c, the breathing hole 141, the floating ball 23, a release mechanism 24b, a fixing ring 25a, a adapter 27, etc.; the breathing hole 141 includes a content chamber 143, the inner micro air hole 221, etc.; the outer shape of the micro valve body 21c is cylindrical, and the micro valve body 21c includes the inner cavity 222, a connection chamber 218, a separation part 213, an outer air hole 227, an outer thread 215, etc.; the breathing hole 141 is installed on the outer wall of the air pressure chamber 14; the inner micro air hole 221 is set at a position where the content chamber 143 deviates from the axis 223 of the inner cavity 222 and is close to the inner ring surface 224, and can communicate with the inside of the air pressure chamber 14. The content chamber 143 has an inner thread; the long cylindrical inner cavity 222 has the axis 223, the inner ring surface 224, the inner end 225 and the outer end 226; the outer ring surface of the inner cavity 222 is provided with the outer thread 215 which can be coupled and sealed with the inner thread of the content chamber 143; the floating ball 23 is installed in the inner cavity 222 and will float with the high-pressure air flow, and the outer diameter d1 of the floating ball 23 is smaller than the inner diameter D2 of the inner cavity 222, d1<D2; the separation part 213 is located in the middle of the micro valve body 21c and separates the inner cavity 222 and the connection chamber 218 at both ends; the outer air hole 227 is installed on the separation part 213 and on the axis 223, and the outer air hole 227 communicates the inner cavity 222 and the connection chamber 218; the inner diameter of the connection chamber 218 is larger than that of the inner cavity 222, and the inner ring surface space of the connection chamber 218 is cylindrical or a cylindrical space with stepped different diameters. The fixing ring 25a and the adapter 27 can be installed by screwing tightly or other fixed sealing methods. The adapter 27 is installed at the open end in the connection chamber 218 and is fixed in a tight-sealing manner and is located outside the fixing ring 25a, used to connect the gas joint 16 and connect the high-pressure gas to the air pressure chamber 14; the cylindrical fixing ring 25a includes a shaft hole 251, an outer ring surface 252 and one or more ventilation holes 253. The outer ring surface 252 has an outer thread and can be installed and fixed on the inner thread at the bottom of the connection chamber 218 and pressed against the separation part 213. The inner diameter of the shaft hole 251 is smaller than the inner diameter of the outer air hole 227, and the ventilation hole 253 will not be blocked by the separation part 213 and can communicate with the outer air hole 227. The fixing ring 25a can be tightened by applying torque with a tool on the groove or concave hole (not shown) at the open end of the connection chamber 218; the outer ring surface 252 of the fixing ring 25a and the inner diameter surface of the connection chamber 218 can also be smooth surfaces, and they are coupled and slidably installed and fixed with a C buckle and a sealing O-ring. The C buckle can be fixed in the annular groove on the inner diameter surface of the inner concave hole (not shown); the structure of the release mechanism 24b has an adjustment shaft 240, the fixing ring 25a, a fixing nut group 244, a micro spring 245, etc.;The adjusting shaft 240 includes an external thread 241, a ball seat 242, and a shaft 243. The disc-shaped ball seat 242, located at one end of the adjusting shaft 240, has a concave spherical surface. The external thread 241 is located at the other end of the adjusting shaft 240, and the shaft 243 is located between the two. The inner diameter of the external vent 227 is larger than the outer diameter of the ball seat 242, allowing the adjusting shaft 240 to move freely back and forth within the inner chamber 222 and the external vent 227.

[0229] During assembly, the retaining ring 25a is first locked inside the connecting chamber 218. The adjusting shaft 240 is first fitted onto the miniature spring 245, and its tail end is passed through the external vent 227 and the shaft hole 251. The ball seat 242 is left on the side of the inner cavity 222. The inner diameter d3 of the external vent 227 is larger than the outer diameter of the ball seat 242, so that the adjusting shaft 240 can move back and forth freely within the inner cavity 222 and the external vent 227. The shaft 243 slides into the shaft hole 251 to support the adjusting shaft 240. The ball seat 242... The outer diameter of 42 is larger than the outer diameter of the shaft 243 and the outer diameter of the miniature spring 242, so that the shaft 243 is fitted into the miniature spring 245, and the miniature spring 245 can be forced tightly between the ball seat 242 and the retaining ring 25a; the external thread 241 of the adjusting shaft 240 passing through the shaft hole 251 of the retaining ring 25a will protrude from the shaft hole 251, and the retaining nut assembly 244 can be installed on the external thread 241 to ensure that the adjusting shaft 240 will not loosen from the position of the retaining ring 25a when filled with high-pressure gas.

[0230] Fourth embodiment

[0231] Please refer to Figure 7A , Figure 7B , Figure 7C , Figure 7D and Figure 7E, the structure of the buffer valve 2d includes: a micro valve body 21d, the breathing hole 141, the floating ball 23, a release mechanism 24c, a fixing ring 25b, a sliding sleeve 26, a adapter 27, etc.; the micro valve body 21d includes the inner cavity 222, a connecting chamber 218, the outer air hole 227, a partition 213 and an external thread 215; the breathing hole 141 includes a content chamber 143, the inner micro air hole 221, etc.; the breathing hole 141 is installed on the outer circumferential wall of the air pressure chamber 14; the inner micro air hole 221 is arranged at a position where the content chamber 143 deviates from the axis line 223 of the inner cavity 222 and is close to the inner ring surface 224, and can communicate with the inside of the air pressure chamber 14. The content chamber 143 has an internal thread; the long cylindrical inner cavity 222 has the axis line 223, the inner ring surface 224, the inner end 225 and the outer end 226; an external thread 215 is installed on the outer circumferential surface of the inner cavity 222 and can be coupled and sealed with the internal thread of the content chamber 143; the floating ball 23 is installed in the inner cavity 222 and floats with the high-pressure air flow, and the outer diameter d1 of the floating ball 23 is smaller than the inner diameter D2 of the inner cavity 222, d1 < D2; the partition 213 is located in the middle of the micro valve body 21d and separates the inner cavity 222 and the connecting chamber 218 at both ends; the outer air hole 227 is installed on the partition 213 and on the axis line 223, and the outer air hole 227 communicates the inner cavity 222 and the connecting chamber 218; the inner diameter of the connecting chamber 218 is larger than that of the inner cavity 222, and the inner ring surface space of the connecting chamber 218 is a cylindrical space or a cylindrical space with stepped different diameters, and the fixing ring 25b and the adapter 27 can be installed by screwing tightly with threads or other fixed sealing methods; the adapter 27 is installed at the open end in the connecting chamber 218 and fixed in a tight sealing manner and is located outside the fixing ring 25b, used to connect the gas joint 16 and connect the high-pressure gas to the air pressure chamber 14; the cylindrical fixing ring 25b includes a central screw hole 254, an outer circumferential surface 252 and one or more ventilation holes 253. The outer circumferential surface 252 has an external thread and can be installed and fixed on the internal thread at the bottom of the connecting chamber 218 and pressed against the partition 213. The inner diameter of the central screw hole 254 is smaller than the inner diameter of the outer air hole 227, and the ventilation hole 253 is not blocked by the partition 213 and can communicate with the outer air hole 227. The fixing ring 25b can be tightened by applying torque with a tool on the groove or concave hole (not shown) at the open end of the connecting chamber 218; the outer circumferential surface of the fixing ring 25b and the inner diameter surface of the connecting chamber 218 can also be smooth surfaces, and the two are coupled and slidably installed and fixed with a C snap ring and a sealing O-ring. The C snap ring can be fixed in the annular groove (not marked) on the inner diameter surface of the connecting chamber 218; the structure of the release mechanism 24c has an adjustment shaft 240, the sliding sleeve 26, the fixing ring 25b, a locking nut 264, a fixing nut group 244, a micro spring 245, etc.;The sliding sleeve 26 includes a sliding shaft hole 261, an adjusting plate 262, and an external thread 263, etc., and the outer diameter of the external thread 263 is larger than the outer diameter of the miniature spring 245 and is coupled to the central thread hole 254; the inner diameter of the external vent 227 is larger than the outer diameter of the ball seat 242, so that the adjusting shaft 240 can move back and forth freely within the inner cavity 222 and the external vent 227.

[0232] During assembly, the retaining ring 25b is first locked inside the connecting chamber 218. The external thread 263 of the sliding sleeve 26 is coupled to the central threaded hole 254. The adjusting shaft 240 is first fitted into the miniature spring 245, and its tail end passes through the external vent 227 and the sliding shaft hole 261. The ball seat 242 is left at the inner cavity 222 end. The outer diameter of the ball seat 242 is smaller than the inner diameter of the external vent 227. The shaft 243 slides into the sliding shaft hole 261 to support the adjusting shaft 240. The outer diameter of the ball seat 242 is larger than the outer diameter of the shaft 243 and the outer diameter of the miniature spring 245. When the shaft 243 is fitted into the miniature spring 245, the miniature spring 245 can be forced tightly between the ball seat 242 and the sliding sleeve 26. The adjusting shaft 240 passes through the sliding shaft hole 261. The external thread 241 of the 0 extends out of the sliding shaft hole 261. The fixing nut assembly 244 can be installed on the external thread 241 to ensure that the adjusting shaft 240 will not loosen from the position of the sliding sleeve 26 when filled with high-pressure gas. The adjusting plate 262 of the sliding sleeve 26 can be rotated to adjust its front and rear position and can be fixed by the locking nut 264. The position of the miniature spring 245 will affect the position of the sliding sleeve 26 and change the compression displacement ΔX. Adjusting the position of the sliding sleeve 26 can finely adjust the compression displacement ΔX of the miniature spring 245 to change the elastic force Fs. Therefore, with the elastic coefficient K of the fixed miniature spring 245 fixed and the outer diameter d1 and weight W of the floating ball fixed, the elastic force Fs can be changed so that the shielding time Δt can be adjusted.

[0233] As described in the third and fourth embodiments, the shielding action 230 occurs when the pressure chamber 14 releases high-pressure gas, causing the floating ball 23 to adhere to the ball seat 242. When the floating ball 23 completes the shielding action, a circular contact line C is formed between the floating ball and the inlet of the external air hole 227. The shielding action 230 is caused by a clamping force Fp generated by the pressure difference ΔP between the gas pressure and the pipeline pressure. This clamping force Fp applies pressure to the floating ball 23 and, through the ball seat 242, clamps and pushes the micro-spring 245, generating a compression displacement ΔX. This compression displacement ΔX is the compression amount of the micro-spring 245. The miniature spring 245 generates the elastic force Fs, Fp≧Fs, and the circular contact line C does not form a sealing surface and therefore cannot achieve an airtight effect, but only reduces the rate of gas leakage; when the outer diameter d1 of the floating ball 23 is greater than the inner diameter d3 of the outer vent, the cone angle 2θ between the circular contact line C generated by the shielding action 230 and the center of the floating ball 23 is 15°≦θ≦80°; when the outer diameter d1 of the floating ball 23 is less than the inner diameter d3 of the outer vent 227, and the annular area of ​​the gap between the outer diameter d1 and the inner diameter d3 is not greater than 50% of the cross-sectional area of ​​the inner micro vent 221, slow gas leakage is achieved (not shown).

[0234] Please refer to Figure 6C , Figure 6E , Figure 7C and Figure 7E The release action 231 occurs when the clamping force Fp generated by the pressure difference ΔP cannot resist the elastic force Fs of the micro spring 245, Fp≦Fs. The floating ball 23 is pushed away and moves to the inner cavity 222, no longer blocking the outer vent 227, allowing the residual high-pressure gas to be released quickly. The elastic force Fs is equal to the product of the compression displacement ΔX and the elastic coefficient K. The release action 231 can be reliably completed because of the ratio of the outer diameter d1 of the floating ball 23 to the inner diameter D2 of the inner cavity 222, d1 / D2≦0.8.

[0235] The adjustment mechanism 28 allows the shielding time Δt to be adjusted by the weight W and size d1 of the floating ball 23 and the elastic force Fs of the miniature spring 245. Specifically, adjusting the position of the sliding sleeve 26 fine-tunes the compression displacement ΔX of the miniature spring 245, thereby changing the elastic force Fs. Adjusting the position of the sliding sleeve 26 is equivalent to adjusting the magnitude of the compression displacement ΔX and the elastic force Fs. Thus, with the elastic coefficient K of the miniature spring 245 fixed, and the outer diameter d1 and weight W of the floating ball also fixed, the shielding time Δt can be changed, thereby adjusting the duration of the shielding time Δt.

[0236] In the first and second embodiments, when the direction of the weight W borne by the floating ball 23 is consistent with the direction of the clamping force Fp, the floating ball 23 will not deviate from the external vent 227 and will be unable to quickly expel residual gas. The release mechanism 24b / 24c / 24d in the third, fourth, or fifth embodiments (described later) can solve this limitation, that is, it eliminates the situation where the direction of the weight W borne by the floating ball 23 is consistent with the direction of the clamping force Fp, which may prevent the rapid expulsion of residual gas. The release mechanism's floating ball weight W, elastic force Fs, magnetic force Fm, and... The clamping force Fp has no directional limitation; in the third embodiment, the fixing nut assembly 244 can be tightly locked onto the fixing ring 25a, applying a pre-compression to the miniature spring 245, so that the fixing shaft 240 is in a stable state unaffected by high-speed filling gas; in the fourth embodiment, the fixing nut assembly 244 can be tightly locked onto the adjusting plate 262 of the sliding sleeve 26, applying a pre-compression to the miniature spring 245, so that the fixing shaft 240 is in a stable state unaffected by high-speed filling gas; the pre-compression can also be used to adjust the elastic force Fs of the miniature spring 245.

[0237] Fifth Embodiment

[0238] Please refer to Figure 8AThe buffer valve 2e is an independent device. Its structure includes a micro-valve body 21e, a breathing cap 20b, and a floating ball 23a. The micro-valve body 21e is cylindrical and comprises an inner chamber 222, an outer chamber 212, an isolation section 213, an external vent 227, and a magnetic body 219. The outer chamber 212 is used to install the gas connector 16. The elongated cylindrical inner chamber 222 has a centerline 223, an inner annular surface 224, an inner end 225, and an outer end 226. The breathing cap 20b connects to the breathing hole 141 and contains an inner micro-gas... The breathing cap 20b includes a hole 221, an inner chamber 202, an external thread 203, and a central post 204; the external thread 203 of the breathing cap 20b can be coupled and sealed with the breathing hole 141; the outer annular surface of the micro-valve body 2e is coupled and sealed with the inner chamber 202 of the breathing cap 20b; the inner micro-vent 221 is offset from the axis 223 of the inner chamber 202 and is located at the inner end 225 and close to the inner annular surface 224, and can communicate with the breathing hole 141; the central post 204 of the breathing cap 20b is installed at the bottom center of the inner chamber 202 and is concentric with the axis 223, and can extend into the inner cavity 222; the float... The floating ball 23a is cylindrical, with a spherical curved surface 232 at its front end and a cylindrical cylinder 233 at its rear end. The cylinder 233 has a cylindrical blind hole 234. A magnetic ring 235 is installed inside the floating ball 23a. The magnetic ring 235 is a long, ring-shaped structure installed close to the spherical curved surface 232. The axis 223 extends through the center of the spherical curved surface 232, and the center of the magnetic ring 235 is concentric with the blind hole 234. The isolation section 213 is located in the middle of the micro-valve body 21e and separates the inner chamber 222 and the outer chamber 212 located at both ends. They are connected by an external vent 227. The external vent 227 is installed on... The isolation section 213 is located on the axis 223 and can connect the inner chamber 222 and the outer chamber 212; the magnetic body 219 is ring-shaped and is installed on the side of the isolation section 213 near the inner chamber 222 and concentric with the outer air hole 227; the floating ball 23a is placed in the inner chamber 222 and can move back and forth on the central column 204; the magnetic ring 235 of the floating ball 23a and the magnetic body 219 of the micro-valve body 21e generate a repulsive magnetic force Fm; the floating ball 23a moves with the airflow in the inner chamber 222, and the outer diameter d1 of the floating ball 23 is smaller than the inner diameter D2 of the inner chamber 222. <D2。

[0239] During the high-filling action 236, when the pressure chamber 14 is filled with high-pressure gas, the airflow 142 of the high-pressure gas will enter the internal flow channel 22 through the high-pressure pipeline 161 and the external air hole 227, and push the floating ball 23a to the inner end 225 of the inner cavity 222 without blocking the internal micro air hole 221, thus maintaining the high-filling action 236 of the high-pressure gas entering the pressure chamber through the internal micro air hole 221.

[0240] When the high-pressure gas is released, the floating ball 23a can perform the shielding action 230 on the outer air hole 227; the shielding action 230 is that when the high-pressure gas is released from the pneumatic chamber 14, the floating ball 23 will adhere to the outer air hole 227, and when the floating ball 23 completes the shielding action 230, a circular contact line C will be formed between the floating ball and the inlet of the outer air hole 227.

[0241] The shielding action 230 is that the magnetic force Fm of mutual repulsion between the magnetic ring 235 of the floating ball 23a and the magnetic body 219 of the micro valve body 21e cannot resist the pressing force Fp generated by the pressure difference ΔP, Fm < Fp, so that the floating ball 23a is fixed to the outer air hole 227.

[0242] When the outer diameter d1 of the floating ball 23a is greater than the inner diameter d3 of the outer air hole, the conical angle 2θ between the circular contact line C generated by the shielding action 230 and the center of the floating ball 23 is 15° ≤ θ ≤ 80°.

[0243] When the outer diameter d1 of the floating ball 23a is smaller than the inner diameter d3 of the outer air hole 227, and the annular area of the gap between the outer diameter d1 and the inner diameter d3 is not more than 50% of the cross-sectional area of the inner micro air hole 221 to achieve slow air release (not shown).

[0244] When the high-pressure gas pressure decreases, the mutual repulsion magnetic force Fm borne by the floating ball 23a overcomes the pressing force Fp to complete the release action 231. The release mechanism is that the pressing force Fp generated by the pressure difference ΔP cannot resist the magnetic force Fm between the magnetic ring and the magnetic body, Fm > Fp, so that the floating ball generates a backward displacement into the inner cavity and no longer shields the outer air hole;

[0245] The release mechanism 24d is not limited by the direction of the weight W of the floating ball and the direction of the pressing force Fp.

[0246] The release action 231 can be completed reliably due to the ratio of the outer diameter d1 of the floating ball 23a to the inner diameter D2 of the inner cavity 222, d1 / D2 ≤ 0.8.

[0247] For the adjustment mechanism 28, the shielding time Δt can be adjusted by the weight W, outer diameter d1 of the floating ball 23a and the mutual repulsion magnetic force Fm, etc. The adjustment mechanism 28 of the magnetic force Fm refers to adjusting the mutual repulsion force between the magnetic ring 235 and the magnetic body 219 of the micro valve body.

[0248] The above embodiments all solve Problem One, Problem Two, Problem Three, Problem Four and Problem Five, and also fully meet Requirement One, Requirement Two, Requirement Three and Requirement Four, achieving the unique requirements for the transportation of clean fluid and particulate suspension fluid.

Claims

1. A buffer valve of a miniature mechanism, which is a two-way valve, wherein the buffer valve is mounted on a pneumatic diaphragm valve, the pneumatic diaphragm valve comprising a pneumatic cylinder, a diaphragm, and a valve seat, the pneumatic cylinder being divided into a pneumatic chamber and a spring chamber by a piston, the spring chamber being equipped with a spring, and the spring chamber and the pneumatic chamber being respectively provided with a breather hole, the breather hole of the pneumatic chamber including an inner chamber, the inner chamber being equipped with a buffer valve and the buffer valve being equipped with a gas connector for filling with high-pressure gas, the buffer valve being used to adjust the flow rate of the breather hole, the buffer valve being used to adjust the release of high-pressure gas in the pneumatic chamber without affecting the filling speed of the high-pressure gas in the pneumatic chamber, and having a tool part located outside the buffer valve for installing or removing the gas connector; The diaphragm has an integral structure comprising a circumferential portion, a central portion, and an elastic portion. The cross-sectional shape of the elastic portion resembles an Ω-shaped arc curve. Its characteristic is that: During the process of a normally closed valve changing from the open state to the closed state and during the process of a normally open valve changing from the closed state to the open state, when high-pressure gas is released, the buffer valve can slow down the pressure shock wave generated by the release of high-pressure gas for a certain period of time. At the same time, the spring in the spring chamber is restricted when it extends and slowly releases its elastic force. In normally closed valves, the approach velocity of the diaphragm to the valve seat is reduced at the center, thus reducing impact and minimizing the violent jetting generated when the valve seat is closed. The reduced speed at which the diaphragm leaves the valve seat at the center of a normally open valve can slow down the generation of local negative pressure and reduce the generation of intense eddies and turbulence. The buffer valve has an internal flow channel comprising an inner micro-orifice, an inner chamber, an outer vent, and a floating ball. The internal flow channel connects to an internal pressure chamber and also to a gas connector of an external high-pressure gas source. The inner chamber has a centerline, an inner annular surface, an inner end, and an outer end. The inner end connects to the pressure chamber via the inner micro-orifice, which is positioned off-center from the centerline and close to the inner annular surface. The outer end of the inner chamber connects to the gas connector via the outer vent, which is positioned along the centerline of the inner chamber. The floating ball is housed within the inner chamber and floats with the high-pressure airflow. The outer diameter d1 of the floating ball is smaller than the inner diameter D2 of the inner chamber. <D2; The buffer valve has the following functions during operation, including a high filling action, a shielding action, a release action, a shielding time Δt, and an adjustment mechanism, wherein the release action includes a release mechanism. High-filling action refers to the high-pressure gas entering the inner chamber through the high-pressure pipeline and external air hole when the pressure chamber is filled with high-pressure gas. This high-pressure gas pushes the floating ball to the inner micro air hole without causing obstruction, thus maintaining the high-pressure gas entering the pressure chamber with high-filling action. The shielding action occurs when the pressure chamber releases high-pressure gas. The high-pressure gas enters the inner chamber through the inner micro-pores and moves the floating ball to the outer pore to shield it, thus slowing down the release of high-pressure gas. The shielding action is achieved by the floating ball and the inner diameter d3 opening of the outer pore forming a circular contact line C. The circular contact line C cannot achieve an airtight effect but only reduces the rate of gas leakage. The shielding action is caused by a pressure difference Δp between the pressure of the gas and the pipeline pressure, which generates a pressing force Fp applied to the floating ball. The pressing force Fp is equal to the pressure difference Δp multiplied by the circular area of the circular contact line C; The release action means that under the shielding action, when the high-pressure gas is continuously released and then the gas pressure decreases later, the shielding action will be released by the release mechanism for the pressing force Fp, causing the floating ball to displace and no longer shield, and allowing the remaining high-pressure gas to be quickly discharged; The release mechanism refers to a mechanism that uses one or more of the weight W of the floating ball, a spring force Fs, and a magnetic force Fm to resist the pressing force Fp and move the floating ball to complete the release action; The shielding time Δt refers to the period from the generation of the shielding action until the completion of the release action, which is called the shielding time Δt; The adjustment mechanism refers to that the length of the shielding time Δt is adjusted through the release mechanism of the release action.

2. The micro-mechanical snubber valve of claim 1, wherein Connecting from the center of the floating ball to the circular contact line C forms a conical angle 2θ.

3. The micro-mechanical snubber valve of claim 1, wherein The circular contact line C is a narrow annular strip structure.

4. The micro-mechanical snubber valve of claim 1, wherein When the outer diameter d1 of the floating ball is smaller than the inner diameter d3 of the outer air hole, d1 < d3, the circular area of the circular contact line C is equal to the cross-sectional area of the outer diameter of the floating ball, and the annular area of the gap between the outer diameter d1 and the inner diameter d3 is not greater than 50% of the cross-sectional area of the inner micro air hole to achieve slow air leakage.

5. The micro-mechanical snubber valve of claim 2, wherein, The length of the shielding time Δt of the shielding action is proportional to the pressing force Fp; the length of the shielding time Δt of the shielding action is proportional to the size of the conical angle 2θ.

6. The micro- mechanism's snubber valve of claim 1, wherein, When the release mechanism uses the weight W of the machine, in the shielding action, the weight W of the floating ball cannot resist the pressing force Fp, so the floating ball is fixed to the outer air hole. In the release mechanism, the pressing force Fp generated by the pressure difference Δp cannot resist the weight W of the floating ball itself, causing the floating ball to displace to the inner cavity and no longer shield the outer air hole.

7. The buffer valve of the micro-mechanism as described in claim 1, characterized in that, When the release mechanism uses the spring force Fs of the machine, in the shielding action, the spring force Fs borne by the floating ball cannot resist the pressing force Fp, so the floating ball is fixed to the outer air hole. In the release mechanism, the pressing force Fp generated by the pressure difference Δp cannot resist the spring force Fs borne by the floating ball, causing the floating ball to displace to the inner cavity and no longer shield the outer air hole.

8. The buffer valve of the micro-mechanism as described in claim 1, characterized in that, When the release mechanism uses the magnetic force Fm of the machine, in the shielding action, the magnetic force Fm borne by the floating ball cannot resist the pressing force Fp, so the floating ball is fixed to the outer air hole. In the release mechanism, the pressing force Fp generated by the pressure difference Δp cannot resist the magnetic force Fm borne by the floating ball, causing the floating ball to displace to the inner cavity and no longer shield the outer air hole.

9. The buffer valve of the micro-mechanism as described in claim 2, characterized in that, The structure of the buffer valve includes: a micro valve body and a breathing hole; The outer shape of the micro valve body is cylindrical, including an inner cavity, an outer cavity, an isolation part, and an outer air hole; The breathing hole includes an inner cavity, an inner micro air hole. The breathing hole is installed on the outer ring wall of the air pressure chamber, and the inner micro air hole is set at a position where the inner cavity deviates from the axis line of the inner cavity and is close to the inner ring surface; the outer ring surface of the micro valve body can be coupled and sealed with the inner cavity of the breathing hole; the outer cavity can be used to install a gas joint; The isolation part is located in the middle of the micro valve body and separates the inner cavity and the outer cavity at both ends. The isolation part is provided with an outer air hole connecting the outer cavity and the inner cavity, and the outer air hole is located on the axis line.

10. The buffer valve of the micro-mechanism as described in claim 2, characterized in that, The structure of the buffer valve includes: a micro valve body and a breathing cover; The micro-valve body is cylindrical in shape and includes an inner chamber, an outer chamber, an isolation section, and an external vent. The breathing cap is used to connect to the breathing hole and includes an inner chamber, an inner micro-vent, and an external thread. The external threads of the breathing cap can couple and seal with the breathing hole; The internal micropores are located on the breathing cover and are offset from the axis of the inner chamber but close to the inner annular surface, so that they can communicate with the breathing holes; The outer annular surface of the micro-valve body is coupled and sealed to the inner chamber of the breathing cap; The outer chamber can be used to install gas fittings; The isolation section is located in the middle of the micro-valve body and separates the inner chamber and the outer chamber at both ends. The isolation section is provided with an external vent that connects the outer chamber and the inner chamber. The external vent is located on the axis.

11. The buffer valve of the micro-mechanism as described in claim 9 or 10, characterized in that, The shielding action occurs when the weight W of the floating ball cannot resist the clamping force Fp generated by the pressure difference Δp, thus fixing the floating ball to the external air hole.

12. The buffer valve of the micro-mechanism as described in claim 9 or 10, characterized in that, The release mechanism is that the weight W of the floating ball itself exceeds the clamping force Fp generated by the pressure difference Δp, causing the floating ball to shift into the inner chamber and no longer block the external air vent.

13. The buffer valve of the micro-mechanism as described in claim 9 or 10, characterized in that, The release mechanism can be reliably completed based on the ratio of the outer diameter d1 of the floating ball to the inner diameter D2 of the inner chamber, where d1 / D2≤0.

6.

14. The buffer valve of the micro-mechanism as described in claim 9 or 10, characterized in that, The outer diameter d1 of the floating ball is greater than the inner diameter d3 of the outer vent, and the cone angle 2θ satisfies 10°≤θ≤60°.

15. The buffer valve of the micro-mechanism as described in claim 9 or 10, characterized in that, The adjustment mechanism involves adjusting the weight W, outer diameter d1, and cone angle 2θ of the floating ball.

16. The buffer valve of the micro-mechanism as described in claim 2, characterized in that, The structure of the buffer valve includes: a micro-valve body, a breather hole, a release mechanism, a retaining ring, and an adapter. The micro-valve body is cylindrical in shape and includes an inner chamber, a connecting chamber, an isolation section and an external vent. The breathing port includes an inner chamber and internal micro-pores, and the breathing port is installed on the outer ring wall of the pressure chamber. The outer annular surface of the micro-valve body can couple and seal with the inner chamber of the breathing hole; The internal micropores are located in the inner chamber, offset from the axis of the inner cavity and close to the inner annular surface; The isolation section is installed between the inner chamber and the connecting chamber, and the isolation section is provided with an external vent that connects the connecting chamber and the inner chamber. The external vent is located on the axis. The inner diameter of the connecting chamber is larger than that of the inner cavity, which can airtightly fix the fixing ring and the adapter; The adapter is installed at the open end of the connecting chamber and is located outside the fixed ring. The adapter is used to connect the gas connector to the high-pressure pipeline and connect to the pressure chamber. The cylindrical retaining ring includes a shaft hole and one or more vent holes. The retaining ring can be installed and fixed at the bottom of the connecting chamber and pressed against the isolation part. The inner diameter of the shaft hole is smaller than the inner diameter of the outer vent hole, and the vent hole can communicate with the outer vent hole. The release mechanism consists of an adjusting shaft, a retaining ring, a set of retaining nuts, and a miniature spring. The adjusting shaft includes an external thread, a ball seat, and a shaft. The disc-shaped ball seat is located at one end of the adjusting shaft and has an inwardly concave spherical surface, while the external thread is located at the other end of the adjusting shaft. During assembly, the retaining ring is first tightened inside the connecting chamber, the adjusting shaft is first fitted with the miniature spring and its tail end is passed through the outer air hole and the shaft hole, leaving the ball seat on the inner chamber side, so that the miniature spring can be fitted on the adjusting shaft and pressed between the ball seat and the retaining ring; the inner diameter of the outer air hole is larger than the outer diameter of the ball seat, so that the adjusting shaft can move back and forth freely in the inner chamber and the outer air hole; The shaft and the shaft hole slide together to support the adjusting shaft; the external thread of the adjusting shaft passing through the shaft hole will extend and be fitted with a set of fixing nuts to ensure that the adjusting shaft will not come loose from the position of the fixing ring when filled with high-pressure gas.

17. The buffer valve of the micro-mechanism as described in claim 2, characterized in that, The structure of the buffer valve includes: a micro-valve body, a breather hole, a release mechanism, a retaining ring, a sliding sleeve, and an adapter. The micro-valve body is cylindrical in shape and includes an inner chamber, a connecting chamber, an isolation section and an external vent. The breathing port includes an inner chamber and internal micro-pores, and the breathing port is installed on the outer ring wall of the pressure chamber. The outer annular surface of the micro-valve body can couple and seal with the inner chamber of the breathing hole; The internal micropores are located in the inner chamber, offset from the axis of the inner cavity and close to the inner annular surface; The isolation section is installed between the inner chamber and the connecting chamber, and the isolation section is provided with an external vent that connects the inner chamber and the connecting chamber. The external vent is located on the axis. The inner diameter of the connecting chamber is larger than that of the inner cavity, which can seal and fix the fixing ring and the airtight adapter. The adapter is installed at the open end of the connecting chamber and is located outside the fixed ring. The adapter is used to connect the gas connector to the high-pressure pipeline and connect to the pressure chamber. The cylindrical retaining ring includes one or more vent holes and a central screw hole. The retaining ring can be installed and fixed at the bottom of the connecting chamber and pressed against the isolation part. The inner diameter of the central screw hole is smaller than the inner diameter of the outer vent hole, and the vent hole can communicate with the outer vent hole. The release mechanism consists of an adjusting shaft, a sliding sleeve, a retaining ring, a locking nut, a set of retaining nuts, and a miniature spring. The adjusting shaft includes an external thread, a ball seat, and a shaft. The disc-shaped ball seat is located at one end of the adjusting shaft and has an inwardly concave spherical surface, while the external thread is located at the other end of the adjusting shaft. The sliding sleeve includes a sliding shaft hole, an adjusting plate, and an external thread; During assembly, the retaining ring is first tightened inside the connecting chamber. The outer thread of the sliding sleeve is first fitted with a locking nut until the position of the adjusting plate, and then coupled with the center thread hole of the retaining ring. The adjusting shaft is first fitted with the miniature spring and its tail end is passed through the outer air hole and the sliding shaft hole. The ball seat is left on the inner chamber side. Moreover, the outer diameter of the outer thread of the sliding sleeve is larger than the outer diameter of the miniature spring, so that the miniature spring can be fitted on the adjusting shaft and pressed between the ball seat and the sliding sleeve. The inner diameter of the outer vent is larger than the outer diameter of the ball seat, allowing the adjusting shaft to move freely back and forth within the inner chamber and the outer vent. The shaft and the sliding hole are in a sliding fit to support the adjusting shaft; The adjusting plate of the sliding sleeve can be rotated to adjust its front and back position and can be fixed with a locking nut. The position of the miniature spring will affect the position of the sliding sleeve and change the compression displacement ΔX. The external thread of the adjusting shaft passing through the sliding shaft hole of the sliding sleeve will extend and be fitted with a fixing nut assembly to ensure that the adjusting shaft will not come loose from the position of the sliding sleeve when high-pressure gas is filled; Adjusting the position of the sliding sleeve finely modifies the compression displacement ΔX of the miniature spring, thereby changing the elastic force Fs. With the elastic coefficient K of the miniature spring fixed, and the outer diameter d1 and weight W of the floating ball also fixed, the elastic force Fs can be changed to adjust the duration of the shielding time Δt.

18. The buffer valve of the micro-mechanism as described in claim 16 or 17, characterized in that, The shielding action is that the high-pressure gas drives the floating ball to closely adhere to the ball seat. The pressure difference Δp generated by the high-pressure gas generates a tightening force Fp applied to the floating ball, and after the ball seat compresses the micro spring, a compression displacement ΔX and an elastic force Fs are generated. The compression displacement ΔX is the compression amount of the micro spring, and Fp≥Fs.

19. The buffer valve of the micro-mechanism as described in claim 16 or 17, characterized in that, The release mechanism is that the tightening force Fp generated by the pressure difference Δp cannot resist the elastic force Fs of the micro spring, and the floating ball is pushed away and moved to the inner cavity and no longer shields the external air hole, Fp≤Fs.

20. The buffer valve of the micro-mechanism as described in claim 16 or 17, characterized in that, The release mechanism is not limited by the direction of the weight W of the floating ball and the direction of the tightening force Fp.

21. The buffer valve of the micro-mechanism as described in claim 16 or 17, characterized in that, The release mechanism can be successfully completed due to the ratio of the outer diameter d1 of the floating ball to the inner diameter D2 of the inner cavity, d1 / D2≤0.

8.

22. The buffer valve of the micro-mechanism as described in claim 16 or 17, characterized in that, The outer diameter d1 of the floating ball is larger than the inner diameter d3 of the external air hole, and the conical angle 2θ satisfies 15°≤θ≤80°.

23. The buffer valve of the micro-mechanism as described in claim 16 or 17, characterized in that, Adjustment mechanism, the shielding time Δt can be adjusted by the weight W, outer diameter d1 of the floating ball and the elastic force Fs, where the adjustment of the elastic force Fs refers to adjusting the elastic coefficient of the micro spring.

24. The buffer valve of the micro-mechanism as described in claim 16 or 17, characterized in that, Adjustment mechanism, including a fixed nut group, can set the relative position of the ball seat of the adjustment shaft relative to the opening of the external air hole on the inner cavity side to ensure that the floating ball can successfully complete the shielding action and the release action.

25. The buffer valve of the micro-mechanism as described in claim 2, characterized in that, The structure of the buffer valve includes: a micro valve body and a breathing cover; The outer shape of the micro valve body is cylindrical, including an inner cavity, an outer cavity, an isolation part, an external air hole and a magnetic body; the outer cavity can be used to install a gas joint; The breathing cover is used to connect the breathing hole, including an inner cavity, an inner micro air hole, an external thread and a central column; the external thread of the breathing cover can be coupled and sealed with the breathing hole; the outer ring surface of the micro valve body is coupled and sealed with the inner cavity of the breathing cover; The central column of the breathing cover is installed at the center of the bottom of the inner cavity and is concentric with the axis and can extend into the inner cavity; The inner micro air hole deviates from the axis of the inner cavity and is located at the inner side end and close to the inner ring surface and can communicate with the breathing hole; The floating ball is cylindrical, with a spherical surface at its front end and a cylinder with a cylindrical blind hole at its rear end. A magnetic ring is installed inside the floating ball. The magnetic ring is long and annular and is installed close to the spherical surface. The axis can extend through the center of the spherical surface, and the center of the magnetic ring and the center of the blind hole are concentric; The isolation part is located in the middle of the micro valve body and separates the inner cavity and the outer cavity at both ends, and is connected by the external air hole. The external air hole is located on the axis; The magnetic body is annular and is installed on the isolation part close to the inner cavity side and is concentric with the external air hole; The floating ball is placed in the inner cavity and can move back and forth on the central column; a repulsive magnetic force Fm is generated between the magnetic ring of the floating ball and the magnetic body of the micro valve body; The shielding action is that the repulsive magnetic force Fm between the floating ball and the micro valve body cannot resist the tightening force Fp generated by the pressure difference Δp, Fm<Fp, and the floating ball is fixed to the external air hole; The release mechanism is that the tightening force Fp generated by the pressure difference Δp cannot resist the repulsive magnetic force Fm between the magnetic ring and the magnetic body, Fm>Fp, causing the floating ball to generate a backward displacement to the inner cavity and no longer shield the external air hole.

26. The buffer valve of the micro-mechanism as described in claim 25, characterized in that, The release mechanism is not limited by the direction of the weight W of the floating ball and the direction of the tightening force Fp.

27. The buffer valve of the micro-mechanism as described in claim 25, characterized in that, The release mechanism can be reliably completed based on the ratio of the outer diameter d1 of the floating ball to the inner diameter D2 of the inner chamber, where d1 / D2 ≤ 0.

9.

28. The buffer valve of the micro-mechanism as described in claim 25, characterized in that, When the outer diameter d1 of the floating ball is greater than the inner diameter d3 of the outer air hole, the cone angle 2θ satisfies 10°≤θ≤80°.

29. The buffer valve of the micro-mechanism as described in claim 25, characterized in that, The adjustment mechanism allows the shielding time Δt to be adjusted by the outer diameter d1 and the magnetic force Fm. The adjustment mechanism of the magnetic force refers to adjusting the mutual repulsion force between the magnetic ring and the micro-valve body.

30. The buffer valve of the micro-mechanism as described in claim 1, characterized in that, The floating ball's weight W, elastic force Fs, magnetic force Fm, and clamping force Fp in the release mechanism have no directional restrictions.

31. The buffer valve of the micro-mechanism as described in claim 1, characterized in that, When a normally closed valve changes from an open state to a closed state, or a normally open valve changes from a closed state to an open state, and when high-pressure gas is released, the buffer valve can be activated immediately. In a normally closed valve, the approach speed of the diaphragm towards the valve seat at the center of the diaphragm immediately decreases, while in a normally open valve, the removal speed of the diaphragm away from the valve seat at the moment of departure immediately decreases.

32. The buffer valve of the micro-mechanism as described in claim 31, characterized in that, In the process of a normally closed valve changing from an open state to a closed state, and in the process of a normally open valve changing from a closed state to an open state, the certain time refers to the shielding time Δt of the buffer valve during the release of high-pressure gas, which slows down the pressure shock wave generated by the release of high-pressure gas throughout the entire process; in the normally closed valve, the approach speed of the diaphragm to the valve seat at the center is reduced throughout the entire process, thereby reducing the impact and reducing the violent jet flow generated when the valve seat is closed; in the normally open valve, the removal speed of the diaphragm from the valve seat at the center is reduced throughout the entire process, which can slow down the generation of local negative pressure and reduce the generation of violent eddies and violent turbulence.

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