Pneumatic diaphragm control valve with multi-stage pressure reduction function

Abstract

This invention discloses a pneumatic diaphragm regulating valve with multi-stage pressure reduction performance, belonging to the field of valve technology. It optimizes the structure of traditional pneumatic diaphragm regulating valves by adding a throttling cage and a perforated throttling plate that cooperate and match with the valve core inside the valve body. When the valve is open, instantaneous hydraulic pressure drives the turbine blades to rotate, which in turn drives the perforated throttling plate to rotate, pre-treating the high-pressure fluid medium. The medium is dynamically diverted upward through the drain ring groove and then swirled laterally through the swirl orifice of the cage to reduce pressure. The throttling mechanism of the perforated plate rotation and the diversion orifice consumes most of the kinetic energy of the medium, achieving multi-stage pressure reduction and promoting stable control under high pressure differential environments. In addition, the valve core, cage, and valve seat with an integral conical mating structure serve as the main valve core sealing structure. When the valve core moves downward, multiple sealing gaskets and sealing rings come into contact in sequence, forming multiple soft and hard sealing barriers, realizing the functions of step-by-step buffer sealing and pressure graded bearing.

Description

Technical Field

[0001] This invention relates to the field of valve technology, and more specifically, to a pneumatic diaphragm control valve with multi-stage pressure reduction capabilities. Background Technology

[0002] A pneumatic diaphragm regulating valve is a control valve specifically designed for high pressure differential and high flow rate scenarios. It mainly consists of a pneumatic actuator and a valve body. The pneumatic actuator receives pneumatic signals from the control system and changes the position of the valve core by controlling the opening and closing of the air source and exhaust port, thereby regulating the flow rate. The valve body is responsible for controlling the flow of the medium and has good corrosion resistance and sealing performance. For details, please refer to the main content of patent publication number CN218326214U.

[0003] However, when the medium pressure is high, especially under high pressure differential, the valve may be subjected to a large pressure differential, which will erode the flow-cutting surface of the valve core, valve body and other internal structures, causing the valve core, valve seat and other components to bear greater pressure, which may cause problems such as noise, increased wear and even leakage. Therefore, the following technical solution is proposed. Summary of the Invention

[0004] The purpose of this invention is to solve existing practical problems. Compared with existing technologies, it provides a pneumatic diaphragm regulating valve with multi-stage pressure reduction performance. A throttling cage and a perforated throttling plate that cooperate with the valve core are added to the valve body. The pressure reduction is enhanced by the transverse swirling flow of fluid. The throttling mechanism of the perforated plate rotation and the diversion orifice are coordinated to achieve multi-stage pressure reduction.

[0005] The objective of this invention can be achieved through the following technical solution: a pneumatic diaphragm regulating valve with multi-stage pressure reduction performance, comprising a valve body and a pneumatic actuator installed in a linkage manner, wherein the valve body is provided with a valve seat, a valve core and a valve stem, and the upper end of the valve stem is connected to the pneumatic actuator through a push rod;

[0006] A sealing seat is fixedly installed at the top of the valve body and movably and sealingly connected to the upper end of the valve stem. A cage sleeve is fixedly installed on the upper part of the valve seat and sleeved outside the valve core. Multiple sets of swirl ports are distributed vertically along the annular direction on the end wall of the cage sleeve. A reserved hole with an opening at the lower end is opened inside the valve core. A linkage shaft is fixedly installed at the top of the reserved hole. An auxiliary throttling component with its bottom end rotatably installed at the flow port of the valve seat is movably sleeved on the outer end of the linkage shaft.

[0007] The auxiliary throttling assembly includes a turbine blade rotatably mounted at the flow port of the valve seat. The rotating end of the turbine blade is fixedly connected to a rotating sleeve that is movably sleeved on the linkage shaft. Multiple perforated throttling plates are fixedly circumferentially on the outer end wall of the rotating sleeve.

[0008] Furthermore, the lower end of the valve core has a conical structure with an outer diameter that gradually decreases from top to bottom, the upper end of the valve core has a cylindrical structure, and it is movably and sealed within the sealing seat. The inner side of the lower end of the cage sleeve is provided with a conical guide cavity that is adapted to the conical structure.

[0009] Furthermore, the swirling orifice has a horizontal cross-section with an L-shaped structure, and the outer opening of the swirling orifice is distributed outwards on the outer wall of the cage. The L-shaped swirling orifice forcibly changes the direction of the medium fluid. When the medium passes through the L-shaped bend, a swirling flow is formed due to the centrifugal force. The friction and collision between the fluid micro-elements further dissipate kinetic energy, reduce the outlet flow velocity, and reduce the impact on the valve body.

[0010] Furthermore, the outer wall of the cage is circumferentially distributed with multiple guide vanes corresponding to the external opening positions of the swirl port, and the outward tilting direction of the guide vanes is consistent with the swirl cutting direction of the external port of the swirl port.

[0011] Furthermore, multiple sealing rings are fixed on the inner wall of the cage-like conical guide cavity, distributed equidistantly from top to bottom. The outer end wall of the valve core is provided with multiple leakage ring grooves from top to bottom, which are adapted to the positions of the sealing rings and whose lower ports are tangent to the edge of the conical outer wall of the valve core. The opening of the leakage ring grooves has a dynamic leakage and diversion function. When the valve core is opened, the leakage ring grooves divert the flow upward step by step and cooperate with the multiple swirling orifices to swirl outwards laterally, thereby achieving step-by-step throttling and pressure reduction and consuming the kinetic energy of the medium. When the valve core moves downward, multiple sealing gaskets and sealing rings come into contact in sequence, forming multiple soft and hard sealing barriers, thereby achieving the functions of step-by-step buffering and sealing and pressure gradation.

[0012] Furthermore, a sealing gasket is embedded in the top of the drain ring groove and is sealed to the upper end of the sealing ring.

[0013] Furthermore, the upper end of the valve seat flow port is provided with an annular sealing sleeve that seals and connects with the lower end of the valve core, and a cross-shaped bracket fixed at the valve seat flow port is provided below the annular sealing sleeve, with the turbine blades rotatably mounted on the cross-shaped bracket.

[0014] Furthermore, the distribution of the multiple perforated throttle plates is consistent with the distribution of the turbine blades, and the perforated throttle plates are provided with multiple throttle holes.

[0015] Compared with the prior art, the advantages of this invention are:

[0016] This solution optimizes the traditional pneumatic diaphragm control valve structure by adding a throttling cage and a perforated throttling plate within the valve body to work in conjunction with the valve core. Specifically, during operation at the valve opening, the pneumatic diaphragm actuator lifts the valve core upwards, instantly causing the turbine blades to rotate. The turbine blades then rotate the perforated throttling plate above, pre-processing the high-pressure fluid and consuming some of the kinetic energy in the medium. As the cage and perforated throttling plate are gradually exposed, the fluid sequentially passes through the various swirling orifices of the cage, resulting in a step-by-step pressure reduction. This, combined with the rotation of the perforated plate and the throttling mechanism of the diversion orifices, achieves multi-stage pressure reduction, reduces the risk of valve core cavitation, and promotes stable control under high pressure differential environments.

[0017] This solution also improves the traditional valve core structure, using an integral conical mating structure of valve core, cage, and valve seat as the main valve core sealing structure. Based on a multi-stage sealing mechanism, the conical surface self-aligns to improve sealing stability. When the valve core moves downward, multiple sealing gaskets and sealing rings come into contact with each other in sequence, forming multiple soft and hard sealing barriers to achieve the functions of step-by-step buffer sealing and pressure graded bearing. The opening of the venting ring groove also has a dynamic venting and diversion function. When the valve core is open, the venting ring groove diverts the flow upward in stages and cooperates with multiple swirl ports to achieve step-by-step throttling and pressure reduction, consume the kinetic energy of the medium, and reduce direct impact on the valve core and valve body. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of the external structure of the present invention;

[0019] Figure 2 This is an internal sectional view of the valve body of the present invention;

[0020] Figure 3 This is a schematic diagram of the structure of the valve seat, sealing seat, and cage sleeve joint of the present invention;

[0021] Figure 4 This is a schematic diagram of the structure when the valve core and the cage sleeve of the present invention are separated;

[0022] Figure 5 This is a horizontal cross-sectional view of the cage sleeve of the present invention;

[0023] Figure 6 This is a schematic diagram of the structure when the valve core and the cage sleeve of the present invention are sealed together.

[0024] Figure 7 This is a schematic diagram of the auxiliary throttling component of the present invention;

[0025] Figure 8 This is a schematic diagram of the structure of the present invention when the valve core is raised to expose the auxiliary throttling component;

[0026] Figure 9 This is a schematic diagram of the medium flow when the valve core is lifted upwards according to the present invention.

[0027] Explanation of the labels in the diagram:

[0028] 1. Valve body; 2. Pneumatic actuator; 3. Push rod; 4. Valve stem; 5. Valve core; 501. Drain ring groove; 502. Sealing gasket; 6. Valve seat; 7. Sealing seat; 8. Cage sleeve; 801. Swirl port; 802. Sealing ring; 9. Guide vane; 10. Turbine blade; 11. Rotating sleeve; 12. Linkage shaft; 13. Perforated throttling plate; 131. Throttling orifice. Detailed Implementation

[0029] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0030] Example 1: This invention discloses a pneumatic diaphragm regulating valve with multi-stage pressure reduction performance. Please refer to [link / reference]. Figures 1-2 It includes a valve body 1 and a pneumatic actuator 2, which are installed in a linkage between the upper and lower parts. The pneumatic actuator 2 consists of a diaphragm chamber, a diaphragm, a spring, and a pneumatic actuation structure.

[0031] The valve body 1 is equipped with a valve seat 6, a valve core 5 and a valve stem 4. The upper end of the valve stem 4 is connected to the pneumatic actuator 2 through a push rod 3. A sealing seat 7 is fixedly installed at the top of the valve body 1 and is movably and sealingly connected to the upper end of the valve stem 4. The valve stem 4 is installed on the upper end of the valve core 5 and passes through the sealing seat 7 to connect with the bottom end of the push rod 3. The valve body 1 controls the push rod 3 to move up and down, thereby driving the valve core 5 to achieve opening and closing through the valve stem 4.

[0032] Please see Figures 3-5 A cage sleeve 8 is fixedly installed on the upper part of the valve seat 6 and sleeved on the outside of the valve core 5. The lower end of the valve core 5 is a conical structure with an outer diameter that gradually decreases from top to bottom. The upper end of the valve core 5 is a cylindrical structure and is movably sealed and connected to the sealing seat 7. A conical guide cavity adapted to the conical structure is opened on the inner side of the lower end of the cage sleeve 8. Multiple sets of swirling ports 801 are distributed in the upper and lower parts along the annular direction on the end wall of the cage sleeve 8. The swirling ports 801 are opened in the conical guide cavity. The swirling ports 801 have a horizontal cross section with an L-shaped structure, and the outer opening of the swirling ports 801 is outwardly spun and distributed on the outer wall of the cage sleeve 8.

[0033] The L-shaped swirl port 801 forcibly changes the direction of the medium fluid. When the medium passes through the L-shaped bend, a swirling flow is formed due to centrifugal force. The friction and collision between fluid micro-particles further dissipate kinetic energy, reduce the outlet flow velocity, and reduce the impact on the valve body.

[0034] The outer wall of the cage 8 has multiple guide vanes 9 distributed in a ring, corresponding to the external opening position of the swirl port 801. The outward tilt direction of the guide vanes 9 is consistent with the swirl direction of the external port of the swirl port 801. The guide vanes 9 can guide the fluid medium discharged from the swirl port 801 to form an ordered swirling flow (such as a forced vortex) rather than a disordered turbulent flow. This swirling flow can prolong the fluid path, increase friction loss, rectify and strengthen the swirling flow, and further improve the throttling pressure drop effect.

[0035] In addition, the guide vane 9, to a certain extent, suppresses the separation vortex that may be generated at the L-shaped bend by constraining the fluid movement, thereby reducing the probability of cavitation. The high-speed fluid passing through the L-shaped opening may generate noise, which can be alleviated by rounding the edge of the guide vane or adding a sound-absorbing structure (such as porous material).

[0036] Please see Figures 6-8 The valve core 5 has a reserved hole with an opening at the lower end. A linkage shaft 12 is fixedly installed at the top of the reserved hole. An auxiliary throttling component with its bottom end rotatably installed at the flow port of the valve seat 6 is movably sleeved at the outer end of the linkage shaft 12.

[0037] The auxiliary throttling assembly includes a turbine blade 10 rotatably mounted at the flow port of the valve seat 6. The rotating end of the turbine blade 10 is fixedly connected to a rotating sleeve 11 movably sleeved on the linkage shaft 12. Both the rotating sleeve 11 and the rotating end of the turbine blade 10 are sealed with low friction seals (such as graphite packing or magnetic fluid seals). Multiple perforated throttling plates 13 are fixed in a ring on the outer end wall of the rotating sleeve 11.

[0038] The upper end of the flow port of valve seat 6 is provided with an annular sealing sleeve that seals with the lower end of valve core 5. Below the annular sealing sleeve is a cross-shaped bracket fixed at the flow port of valve seat 6. Turbine blade 10 is rotatably mounted on the cross-shaped bracket. The distribution of multiple perforated throttling plates 13 is consistent with the distribution of turbine blade 10. Multiple throttling holes 131 are opened on the perforated throttling plates 13.

[0039] An auxiliary throttling component extending to the flow port of the valve seat 6 is added inside the cage sleeve 8. During operation at the open position, the valve core is lifted upward by a pneumatic diaphragm actuator, which instantly hydraulically drives the turbine blades 10 to rotate. The rotation of the turbine blades 10 can, on the one hand, offset part of the kinetic energy of the fluid medium, and on the other hand, drive the upper porous throttling plate 13 to rotate, pre-treating the high-pressure fluid medium and consuming part of the kinetic energy in the medium. After the porous throttling plate 13 is gradually exposed, it has a dynamic throttling effect, specifically:

[0040] When the fluid impacts the porous throttling plate 13 through the flow port and drives it to rotate, the position of the throttling orifice 131 changes continuously with the rotation, causing the fluid to frequently adjust its flow path. This dynamic change increases local eddies and frictional resistance. By dispersing the pressure drop through the small aperture, the fluid's kinetic energy is consumed and noise is absorbed, thus indirectly achieving the throttling effect.

[0041] During the gradual opening of valve core 5, the fluid is discharged laterally through the exposed swirl ports 801 in sequence. The pressure is reduced step by step through the various swirl ports 801 of the cage sleeve. The fluid swirl enhances the pressure reduction, and the throttling mechanism of the multi-hole plate rotation and the diversion orifice is coordinated. The multi-hole throttling plate and the throttling cage sleeve bear the main pressure difference, realize multi-stage pressure reduction, reduce the risk of valve core cavitation, and promote stable control in high pressure differential environment.

[0042] Example 2: Based on Example 1, this example further optimizes and improves the sealing surface structure formed by the cage sleeve 8 and the valve core 5, as follows:

[0043] Please see Figure 4 , Figure 6 as well as Figure 8 , Figure 9 The outer wall of the cage sleeve 8 is provided with a number of guide vanes 9 that correspond to the external opening positions of the swirl port 801. The outward tilting direction of the guide vanes 9 is consistent with the swirl cutting direction of the external port of the swirl port 801. The inner wall of the conical guide cavity of the cage sleeve 8 is fixed with a number of sealing rings 802 that are equidistantly distributed from top to bottom. The outer end wall of the valve core 5 is provided with a number of leakage ring grooves 501 that are adapted to the positions of the sealing rings 802 and whose lower ports are tangent to the edge of the conical outer wall of the valve core 5.

[0044] A sealing gasket 502 is embedded in the top of the drain ring groove 501 and is connected to the upper end of the sealing ring 802. The traditional valve core 5 structure is improved. The valve core 5, cage 8 and valve seat 6 with an integral conical mating structure are used as the main valve core sealing structure. Based on the multi-stage sealing mechanism, the conical surface self-alignment is used to improve the sealing stability. When the valve core 5 moves downward, multiple sealing gaskets 502 (such as PTFE or graphite composite material) come into contact with the sealing ring 802 of the cage 8 (such as stainless steel or hard alloy) in sequence to form multiple soft and hard sealing barriers, realizing the functions of step-by-step buffer sealing and pressure grade bearing.

[0045] The opening of the venting ring groove 501 also has a dynamic venting and diversion function. When the valve core 5 is opened, the fluid medium preferentially flows upward through the gradually exposed venting ring groove 501 and is discharged laterally outward through the swirl port 801. Through the upward diversion of the venting ring groove 501 and the outward swirl design of multiple swirl ports 801, the step-by-step throttling and pressure reduction is further realized, the kinetic energy of the medium is consumed, and the direct impact on the valve core and valve body is reduced.

[0046] In summary: Based on the traditional pneumatic diaphragm control valve structure, a throttling cage and a perforated throttling plate are added to the valve body to cooperate with the valve core. Specifically, during the opening operation, the pneumatic diaphragm actuator lifts the valve core upward, and the instantaneous hydraulic pressure drives the turbine blade 10 to rotate. The turbine blade 10 drives the perforated throttling plate 13 above to rotate, pre-processing the high-pressure fluid and consuming part of the kinetic energy in the medium. After the cage and perforated throttling plate are gradually exposed, the fluid passes through the various swirl ports 801 of the cage 8 in sequence to reduce pressure step by step. The fluid swirl enhances the pressure reduction, and the rotation of the perforated plate and the throttling mechanism of the diversion holes are coordinated. The perforated throttling plate and the throttling cage bear the main pressure difference, realize multi-stage pressure reduction, reduce the risk of valve core cavitation, and promote stable control in high pressure differential environments.

[0047] The valve core 5, cage 8, and valve seat 6, with their integral conical mating structure, serve as the main valve core sealing structure. Based on a multi-stage sealing mechanism, the conical surface self-aligns to improve sealing stability. When the valve core 5 moves downward, multiple sealing gaskets 502 and sealing rings 802 come into contact sequentially, forming multiple soft and hard sealing barriers. This achieves the functions of step-by-step buffering and pressure grading. The opening of the venting ring groove 501 also has a dynamic venting and diversion function. When the valve core 5 is open, the fluid preferentially flows upward through the gradually exposed venting ring groove 501 and is discharged laterally outward through the swirl port 801, achieving step-by-step throttling and pressure reduction, consuming the kinetic energy of the medium, and reducing direct impact on the valve core and valve body.

[0048] The above are merely preferred embodiments of the present invention; however, the scope of protection of the present invention is not limited thereto; any equivalent substitutions or modifications made by those skilled in the art within the technical scope disclosed in the present invention, based on the technical solution and its improved concept, should be covered within the scope of protection of the present invention.

Claims

1. A pneumatic diaphragm regulating valve with multi-stage pressure reduction performance, comprising a valve body (1) and a pneumatic actuator (2) installed in a linkage manner, wherein the valve body (1) is provided with a valve seat (6), a valve core (5) and a valve stem (4), and the upper end of the valve stem (4) is connected to the pneumatic actuator (2) through a push rod (3), characterized in that: A sealing seat (7) is fixedly installed at the top of the valve body (1) and movably and sealingly connected to the upper end of the valve stem (4). A cage sleeve (8) is fixedly installed on the upper part of the valve seat (6) and sleeved outside the valve core (5). Multiple sets of swirling orifices (801) are distributed in the upper and lower parts along the annular direction on the end wall of the cage sleeve (8). A reserved hole with a lower opening is opened inside the valve core (5). A linkage shaft (12) is fixedly installed at the top of the reserved hole. An auxiliary throttling component with a bottom rotatably installed at the flow port of the valve seat (6) is movably sleeved on the outer end of the linkage shaft (12). Among them, the auxiliary throttling component includes a turbine blade (10) rotatably installed at the flow port of the valve seat (6), and a rotating sleeve (11) movably sleeved on the linkage shaft (12) is fixedly connected to the rotating end of the turbine blade (10). Multiple perforated throttling plates (13) are fixedly circumferentially on the outer end wall of the rotating sleeve (11). The lower end of the valve core (5) is a conical structure with an outer diameter that gradually decreases from top to bottom. The upper end of the valve core (5) is a cylindrical structure and is movably sealed and connected to the sealing seat (7). The inner side of the lower end of the cage (8) is provided with a conical guide cavity that is compatible with the conical structure.

2. The pneumatic diaphragm regulating valve with multi-stage pressure reduction performance according to claim 1, characterized in that: The swirling inlet (801) has an L-shaped horizontal cross-section, and the external opening of the swirling inlet (801) is distributed outwardly on the outer wall of the cage (8).

3. The pneumatic diaphragm regulating valve with multi-stage pressure reduction performance according to claim 2, characterized in that: The outer wall of the cage (8) is circumferentially distributed with multiple guide vanes (9) corresponding to the external opening position of the swirl port (801), and the outward tilting direction of the guide vanes (9) is consistent with the swirl cutting direction of the external port of the swirl port (801).

4. The pneumatic diaphragm regulating valve with multi-stage pressure reduction performance according to claim 3, characterized in that: The inner wall of the conical guide cavity of the cage (8) is fixed with a plurality of sealing rings (802) distributed at equal intervals from top to bottom. The outer end wall of the valve core (5) is provided with a plurality of drain ring grooves (501) that are adapted to the position of the sealing rings (802) and whose lower port is tangent to the edge of the conical outer wall of the valve core (5).

5. The pneumatic diaphragm regulating valve with multi-stage pressure reduction performance according to claim 4, characterized in that: A sealing gasket (502) is embedded in the top of the drain ring groove (501) and is connected to the upper end of the sealing ring (802).

6. The pneumatic diaphragm regulating valve with multi-stage pressure reduction performance according to claim 1, characterized in that: The upper end of the flow port of the valve seat (6) is provided with an annular sealing sleeve that seals with the lower end of the valve core (5). Below the annular sealing sleeve is a cross-shaped bracket fixed at the flow port of the valve seat (6). The turbine blade (10) is rotatably mounted on the cross-shaped bracket.

7. The pneumatic diaphragm regulating valve with multi-stage pressure reduction performance according to claim 1, characterized in that: The distribution of the multiple perforated throttle plates (13) is consistent with the distribution of the turbine blades (10), and the perforated throttle plates (13) are provided with multiple throttle holes (131).

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