A double acting diaphragm flow amplifier

Abstract

The utility model discloses an industrial flow control field's double -acting diaphragm type flow amplifier, including organism, double diaphragm subassembly, valve core no.

Description

Technical Field

[0001] This utility model relates to the field of industrial flow control, and in particular to a double-acting diaphragm flow amplifier. Background Technology

[0002] Automatic control valves are an important component of industrial automation instrumentation. Valve positioners, as key control accessories for control valves, significantly improve valve control characteristics, enhancing control accuracy, response speed, and flexibility. The pressure generated by the electrical conversion module in the valve positioner is typically 0.015–1.0 kg / cm². 2 The circuit pressure of the pneumatic actuator of the positioner typically needs to be 1.4–7.0 kg / cm². 2 Therefore, pressure-flow amplifiers are needed to coordinate them. Pressure-flow amplifiers, also known as pneumatic amplifiers, are essentially micro-pressure control elements. They use a very low-pressure, low-flow-rate air pressure signal as the input control signal to obtain a high-pressure, high-flow-rate air pressure signal capable of driving pneumatic actuators.

[0003] Pressure and flow amplifiers can be classified into several types according to their structure, including diaphragm type, diaphragm cutoff type, diaphragm slider type, and diaphragm slide column type; according to their internal air resistance, they can be classified into adjustable amplifiers and non-adjustable amplifiers; and according to their performance, they can be classified into on / off amplifiers and proportional amplifiers. Diaphragm proportional amplifiers are generally used in valve positioners. However, these amplifiers have only one output port and can only be matched with electrical conversion modules (also known as IP modules) within a specific pressure range. If the compressed air pressure output by the electrical conversion module is relatively high, it cannot be used. Utility Model Content

[0004] To address the aforementioned problems in the existing technology, this utility model provides a double-acting diaphragm flow amplifier. It regulates the flow and pressure of two air paths through the linear reciprocating motion of a double diaphragm assembly, making it applicable to a wider range of scenarios. By introducing output air into the double diaphragm assembly, it offsets part of the pressure of the regulating air, thereby achieving a pressure reduction function. There is no need to set up a separate pressure reduction device, so the overall structure is simpler.

[0005] The technical solution of this utility model is as follows:

[0006] A double-acting diaphragm flow amplifier includes a body 1, a double diaphragm assembly 2, a valve core 3, a valve core 2 4, a coil spring 5, and a coil spring 2 6.

[0007] The body 1 is provided with 6 chambers: regulating chamber 7, air inlet chamber 8, air outlet chamber 9, regulating chamber 2 10, air inlet chamber 2 11, and air outlet chamber 2 12; air inlet chamber 8 and air outlet chamber 9 are connected by a through hole, which is called valve 13; air inlet chamber 2 11 and air outlet chamber 2 12 are connected by a through hole, which is called valve 2 14;

[0008] The body 1 is equipped with 5 pipes: air inlet 15, air outlet 16, air inlet 2 17, air outlet 2 18, and IP air inlet 19.

[0009] One end of the intake duct 15 is connected to the intake chamber 8, and the other end of the intake duct 15 is connected to the outside. Compressed air from the outside flows into the intake chamber 8 through the intake duct 15. One end of the exhaust duct 16 is connected to the exhaust chamber 9, and the other end of the exhaust duct 16 is connected to the outside. Compressed air from the exhaust chamber 9 flows out to the outside through the exhaust duct 16.

[0010] One end of the second air intake duct 17 is connected to the second air intake chamber 11, and the other end of the second air intake duct 17 is connected to the outside. Compressed air from the outside flows into the second air intake chamber 11 through the second air intake duct 17. One end of the second air outlet duct 18 is connected to the second air outlet chamber 12, and the other end of the second air outlet duct 18 is connected to the outside. Compressed air from the second air outlet chamber 12 flows out to the outside through the second air outlet duct 18.

[0011] One end of the IP air intake duct 19 is connected to the second regulating chamber 10, and the other end of the second air intake duct 17 is connected to the outside. Compressed air from the outside flows into the second regulating chamber 10 from the IP air intake duct 19.

[0012] The compressed air flowing into intake duct 15 and intake duct 2 17 is called input air, the compressed air flowing into intake duct 19 is called regulating air, and the compressed air flowing out of exhaust duct 16 and exhaust duct 2 18 is called output air.

[0013] The cross-sectional view of the valve core 3 is a T-shaped structure. The valve core 3 is obtained by rotating the T-shaped structure around its own axis of symmetry. The larger diameter top of the valve core 3 is called the valve stop 301, and the rod-shaped part with a smaller diameter than the valve stop 301 is called the ejector pin 302. The valve core 3 is located between the intake chamber 8 and the exhaust chamber 9. The ejector pin 302 passes through the valve 13, and the central axis of the ejector pin 302 coincides with the central axis of the valve 13. The valve core 3 can move linearly along the central axis of the valve 13. The helical spring 5 is located inside the exhaust chamber 9 and pushes the valve core 3 towards the intake chamber 8, so that the valve stop 301 is pressed against the valve 13. When the valve stop 301 is stationary on the valve 13, the intake chamber 8 and the exhaust chamber 9 are not connected, and compressed air cannot flow from the intake chamber 8 to the exhaust chamber 9.

[0014] The structure of valve core 2 4 is the same as that of valve core 1 3, including valve stop 401 and ejector pin 402; valve core 2 4 is located between intake chamber 2 11 and outlet chamber 2 12, ejector pin 402 passes through valve core 2 14, and the central axis of ejector pin 402 coincides with the central axis of valve core 2 14; valve core 4 can move linearly along the central axis of valve core 2 14; the helical spring 2 6 is located inside outlet chamber 2 12, pushing valve core 2 4 towards intake chamber 2 11, so that valve stop 401 is pressed against valve core 2 14; when valve stop 401 is stationary on valve core 2 14, intake chamber 2 11 and outlet chamber 2 12 are not connected, and compressed air cannot flow from intake chamber 2 11 to outlet chamber 2 12;

[0015] The central axis of valve 13 coincides with the central axis of valve 14.

[0016] The dual diaphragm assembly 2 includes a piston rod 20, a flexible diaphragm 1 21, a flexible diaphragm 22, a flexible diaphragm 3 23, and a flexible diaphragm 4 24; the piston rod 20 is a round rod structure, and the central axis of the piston rod 20 coincides with the central axis of the valve 13; the flexible diaphragms 1 21, 2 22, 3 23, and 4 24 are all thin sheet structures and are all fixed on the piston rod 20, and the thickness direction of the four is parallel to the central axis of the piston rod 20;

[0017] The dual diaphragm assembly 2 is positioned between valve 13 and valve 24, and the central axis of piston rod 20 coincides with the central axis of valve 13; the flexible diaphragm 4 24 is fixed to the body 1, forming an intake chamber 2 11 together with the body 1; the flexible diaphragm 3 23 is fixed to the body 1, forming an adjustment chamber 2 10 together with the body 1; the flexible diaphragm 22 is fixed to the body 1, forming an adjustment chamber 1 7 together with the flexible diaphragm 3 23; the flexible diaphragm 1 21 is fixed to the body 1, forming an intake chamber 1 8 together with the body 1; observing along the central axis of piston rod 20, the arrangement order of the above mechanisms is: exhaust chamber 1 9, valve core 1 3, intake chamber 1 10, flexible diaphragm 1 21, flexible diaphragm 22, flexible diaphragm 3 23 and flexible diaphragm 4 24, intake chamber 2 11, valve core 2 4, exhaust chamber 2 12;

[0018] After the regulating air flows into the regulating chamber 10 from the intake passage 19, the pressure inside the regulating chamber 10 increases, the flexible diaphragm 23 deforms and pushes the piston rod 20 towards the intake chamber 10; the valve core 4's ejector pin 402 remains in contact with the piston rod 20, and the valve core 4 moves closer to the valve 14 under the push of the coil spring 6; the closer the valve core 4 is to the valve 14, the less compressed air flows from the intake chamber 11 into the exhaust passage 18; the valve core 4... When valve stem 401 contacts valve 14, the flow rate of compressed air from intake chamber 11 into outlet passage 18 reaches its minimum value; after piston rod 20 contacts valve core 3's ejector pin 302, piston rod 20 pushes valve core 3, causing valve stem 301 of valve core 3 to move away from valve 13, and compressed air flows from intake chamber 10 into outlet passage 16; the greater the distance between valve core 3 and valve 13, the more compressed air flows into outlet passage 16;

[0019] Reducing the amount of regulating air inside regulating chamber 2 10 decreases the pressure inside chamber 2 10, causing piston rod 20 to move closer to intake chamber 2 10; valve core 3's ejector pin 302 remains in contact with piston rod 20, and valve core 3 moves closer to valve 13 under the push of coil spring 5; the closer valve stop 301 is to valve 13, the less compressed air flows from intake chamber 10 into exhaust passage 16; when valve stop 301 is closer to valve 13... When contact occurs, the amount of compressed air flowing from the intake chamber 10 into the exhaust passage 16 reaches a minimum. After the valve core 4's ejector pin 402 contacts the piston rod 20, the valve core 4 is pushed by the piston rod 20, causing the valve stop 401 of the valve core 4 to move away from the valve, and the compressed air flows from the intake chamber 11 into the exhaust passage 18. The greater the distance between the valve stop 401 of the valve core 4 and the valve 14, the more compressed air flows into the exhaust passage 18.

[0020] Furthermore, the air outlet 16 is connected to the regulating chamber 7.

[0021] Furthermore, the flexible diaphragm 21, the flexible diaphragm 22, and the body 1 form a cavity called the exhaust cavity 25; the exhaust cavity 25 is connected to the outside.

[0022] The piston rod 20 is a hollow cylindrical structure and has a through hole, called the exhaust hole 26; the central axis of the exhaust hole 26 is perpendicular to the central axis of the piston rod 20, and the exhaust hole 26 is located inside the exhaust chamber 25.

[0023] Furthermore, a helical spring 27 is provided inside the first air intake chamber 8; one end of the helical spring 27 contacts the body 1, and the other end contacts the piston rod 20, and applies a thrust to the piston rod 20 pointing towards the second air intake chamber 11.

[0024] The air intake chamber 21 is equipped with a helical spring 4 28; one end of the helical spring 4 28 is in contact with the body 1, and the other end is in contact with the piston rod 20, and applies a thrust to the piston rod 20 pointing towards the air intake chamber 1 8.

[0025] Furthermore, the air intake duct 15 is provided with an adjusting bolt 29; rotating the adjusting bolt 29 will change the cross-sectional area of ​​the air intake duct 15.

[0026] The second air intake duct 17 is equipped with an adjusting bolt 30; rotating the adjusting bolt 30 will change the cross-sectional area of ​​the second air intake duct 17.

[0027] Furthermore, the air outlet chamber 9 is provided with an adjusting bolt 31; one end of the helical spring 5 is in contact with the adjusting bolt 31, and the other end is in contact with the valve core 3; rotating the adjusting bolt 31 will change the thrust applied by the helical spring 5 to the valve core 3.

[0028] The second air outlet chamber 11 is equipped with an adjusting bolt 4 32; one end of the second helical spring 6 is in contact with the adjusting bolt 4 32, and the other end is in contact with the valve core 2 4; rotating the adjusting bolt 4 32 will change the thrust applied by the helical spring 2 6 to the valve core 2 4.

[0029] The beneficial technical effects of this utility model are as follows:

[0030] (1) It can control the pressure and flow rate of two gas paths at the same time, making it applicable to a wider range of scenarios;

[0031] (2) The output air is introduced into the double diaphragm assembly to offset part of the pressure of the regulating air, thereby realizing the pressure reduction function. There is no need to set up a separate pressure reduction device, and the overall structure is simpler. Attached Figure Description

[0032] Figure 1 This is an appearance drawing of an embodiment;

[0033] Figure 2 This is a cross-sectional view of an embodiment.

[0034] In the diagram, the correspondence between the component names and the attached drawing numbers is as follows: 1. Body; 2. Dual diaphragm assembly; 3. Valve core one; 4. Valve core two; 5. Coil spring one; 6. Coil spring two; 7. Adjustment chamber one; 8. Intake chamber one; 9. Exit chamber one; 10. Adjustment chamber two; 11. Intake chamber two; 12. Exit chamber two; 13. Valve one; 14. Valve two; 15. Intake duct one; 16. Exit duct one; 17. Intake duct two; 18. Exit duct two; 19. IP intake duct 20. Piston rod; 21. Flexible diaphragm one; 22. Flexible diaphragm two; 23. Flexible diaphragm three; 24. Flexible diaphragm four; 25. Exhaust chamber; 26. Exhaust port; 27. Coil spring three; 28. Coil spring four; 29. ​​Adjusting bolt one; 30. Adjusting bolt two; 31. Adjusting bolt three; 32. Adjusting bolt four; 301. Valve stop of valve core one; 302. Valve pin of valve core one; 401. Valve stop of valve core two; 402. Valve pin of valve core two. Detailed Implementation

[0035] The present invention will now be described in detail with reference to the accompanying drawings and embodiments. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of them. 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.

[0036] The structure of the embodiment is as follows Figure 1 , 2 As shown, the basic principle is to use compressed air from the electrical conversion module (also known as the IP module) as regulating air to drive a diaphragm mechanism, which in turn pushes two valve cores, thereby changing the output airflow of the two air paths.

[0037] The embodiment mainly consists of a body 1, a double diaphragm assembly 2, a valve core 1 3, a valve core 2 4, a coil spring 1 5, and a coil spring 2 6.

[0038] The machine body 1 has six chambers: regulating chamber 7, intake chamber 8, exhaust chamber 9, regulating chamber 2 10, intake chamber 2 11, and exhaust chamber 2 12. Intake chamber 1 8 and exhaust chamber 1 9 are connected by a through hole, which is called valve 1 13; intake chamber 2 11 and exhaust chamber 2 12 are connected by a through hole, which is called valve 2 14. By blocking these two valves with a valve core, the compressed air flow rate of the two air passages can be adjusted.

[0039] The main body 1 is also equipped with 5 pipes: air intake duct 15, air outlet duct 16, air intake duct 2 17, air outlet duct 2 18, and IP air intake duct 19.

[0040] One end of the intake duct 15 is connected to the intake chamber 8, and the other end of the intake duct 15 is connected to the outside. Compressed air from the outside flows into the intake chamber 8 through the intake duct 15. One end of the exhaust duct 16 is connected to the exhaust chamber 9, and the other end of the exhaust duct 16 is connected to the outside. Compressed air from the exhaust chamber 9 flows out to the outside through the exhaust duct 16.

[0041] One end of the second air intake duct 17 is connected to the second air intake chamber 11, and the other end of the second air intake duct 17 is connected to the outside. Compressed air from the outside flows into the second air intake chamber 11 through the second air intake duct 17. One end of the second air outlet duct 18 is connected to the second air outlet chamber 12, and the other end of the second air outlet duct 18 is connected to the outside. Compressed air from the second air outlet chamber 12 flows out to the outside through the second air outlet duct 18.

[0042] One end of the IP intake duct 19 is connected to the regulating chamber 2 10, and the other end of the intake duct 2 17 is connected to the outside. Compressed air from the outside flows into the regulating chamber 2 10 from the IP intake duct 19.

[0043] The compressed air flowing into intake duct 15 and intake duct 2 17 is called input air, the compressed air flowing into intake duct 19 is called regulating air, and the compressed air flowing out of exhaust duct 16 and exhaust duct 2 18 is called output air.

[0044] The cross-sectional view of valve core 3 shows a T-shaped structure, which is obtained by rotating the T-shaped structure around its own axis of symmetry. The larger diameter top of valve core 3 is called valve stop 301, and the rod-shaped portion with a smaller diameter than valve stop 301 is called ejector pin 302. Valve core 3 is positioned between intake chamber 8 and exhaust chamber 9. Ejector pin 302 penetrates valve 13, and the central axis of ejector pin 302 coincides with the central axis of valve 13. Valve core 3 can move linearly along the central axis of valve 13. A coil spring 5 is located inside exhaust chamber 9, pushing valve core 3 towards intake chamber 8, causing valve stop 301 to press against valve 13. When valve stop 301 is in position on valve 13, intake chamber 8 and exhaust chamber 9 are not connected, and compressed air cannot flow from intake chamber 8 to exhaust chamber 9.

[0045] Valve core 2 (4) has the same structure as valve core 1 (3), including valve stop 401 and ejector pin 402. Valve core 2 (4) is located between intake chamber 2 (11) and outlet chamber 2 (12). Ejector pin 402 passes through valve core 2 (14), and the central axis of ejector pin 402 coincides with the central axis of valve core 2 (14). Valve core 4 can move linearly along the central axis of valve core 2 (14). Coil spring 2 (6) is located inside outlet chamber 2 (12), pushing valve core 2 (4) towards intake chamber 2 (11), causing valve stop 401 to press against valve core 2 (14). When valve stop 401 is in position on valve core 2 (14), intake chamber 2 (11) and outlet chamber 2 (12) are not connected, and compressed air cannot flow from intake chamber 2 (11) to outlet chamber 2 (12).

[0046] The central axis of valve 13 coincides with the central axis of valve 2 14.

[0047] The dual diaphragm assembly 2 includes a piston rod 20, a first flexible diaphragm 21, a second flexible diaphragm 22, a third flexible diaphragm 23, and a fourth flexible diaphragm 24. The piston rod 20 is a round rod structure, and its central axis coincides with the central axis of the valve 13. The first flexible diaphragm 21, the second flexible diaphragm 22, the third flexible diaphragm 23, and the fourth flexible diaphragm 24 are all thin sheet structures and are all fixed to the piston rod 20, and the thickness direction of all four is parallel to the central axis of the piston rod 20.

[0048] The dual diaphragm assembly 2 is positioned between valve 13 and valve 24, with the central axis of piston rod 20 coinciding with the central axis of valve 13. Flexible diaphragm 4 24 is fixed to the body 1, forming intake chamber 2 11 together with the body 1; flexible diaphragm 3 23 is fixed to the body 1, forming adjustment chamber 2 10 together with the body 1; flexible diaphragm 2 22 is fixed to the body 1, forming adjustment chamber 1 7 together with flexible diaphragm 3 23; flexible diaphragm 1 21 is fixed to the body 1, forming intake chamber 1 8 together with the body 1. Observing along the central axis of piston rod 20, the arrangement of the above mechanisms is as follows: exhaust chamber 1 9, valve core 1 3, intake chamber 1 10, flexible diaphragm 1 21, flexible diaphragm 2 22, flexible diaphragm 3 23 and flexible diaphragm 4 24, intake chamber 2 11, valve core 2 4, and exhaust chamber 2 12.

[0049] A helical spring 27 is installed inside intake chamber 1. One end of helical spring 27 contacts the body 1, and the other end contacts the piston rod 20, applying a thrust to the piston rod 20 in the direction of intake chamber 11. A helical spring 28 is installed inside intake chamber 11. One end of helical spring 28 contacts the body 1, and the other end contacts the piston rod 20, applying a thrust to the piston rod 20 in the direction of intake chamber 8. The function of helical springs 27 and 28 is to provide a force for the double diaphragm assembly 2 to return to its original position.

[0050] Flexible diaphragm 21, flexible diaphragm 22, and body 1 form a cavity called exhaust chamber 25. Exhaust chamber 25 is connected to the outside. Piston rod 20 is a hollow cylindrical structure and has a through hole called exhaust port 26. The central axis of exhaust port 26 is perpendicular to the central axis of piston rod 20, and exhaust port 26 is located inside exhaust chamber 25. When piston rod 20 disengages from valve core 3, compressed air inside intake chamber 8 flows into piston rod 20 and out to the outside through exhaust port 26.

[0051] The second air intake duct 17 is equipped with an adjusting bolt 30. Rotating the adjusting bolt 30 changes the cross-sectional area of ​​the second air intake duct 17, thus changing the flow rate of the input air flowing from the second air intake duct 17 into the second air intake chamber 11. In this way, the pressure and flow rate of the output air can be finely adjusted.

[0052] An adjusting bolt 31 is provided in the exhaust chamber 19. One end of the coil spring 5 contacts the adjusting bolt 31, and the other end contacts the valve core 3. Rotating the adjusting bolt 31 changes the thrust applied by the coil spring 5 to the valve core 3. An adjusting bolt 4 32 is provided in the exhaust chamber 21. One end of the coil spring 6 contacts the adjusting bolt 4 32, and the other end contacts the valve core 4. Rotating the adjusting bolt 4 32 changes the thrust applied by the coil spring 6 to the valve core 4. In this way, the relationship curve between the regulating air and the output air can be finely adjusted.

[0053] The outlet duct 16 and the regulating chamber 7 are connected, so a portion of the output air flowing from the outlet duct 16 will flow into the regulating chamber 7. As the regulating air inside the regulating chamber 10 gradually increases, the dual diaphragm assembly 2 gradually moves towards the intake chamber 8, the valve core 3 gradually moves away from the valve 13, and the output air flowing into the outlet chamber 9 and outlet duct 16 increases, raising the pressure in the outlet duct 16. This, in turn, raises the pressure inside the regulating chamber 7. The regulating chamber 7 and the regulating chamber 10 are adjacent, separated only by a flexible diaphragm 22. Therefore, the pressure inside the regulating chamber 7 will counteract the pressure inside the regulating chamber 10, thereby weakening the thrust of the regulating air on the dual diaphragm assembly 2 and achieving a pressure reduction effect. This pressure reduction effect allows the embodiment to be matched with electrical conversion modules with relatively high output air pressure.

[0054] The working principle of the embodiment is as follows:

[0055] After the regulating air flows into the regulating chamber 10 from the intake passage 19, the pressure inside the regulating chamber 10 increases, the flexible diaphragm 23 deforms and pushes the piston rod 20 towards the intake chamber 10; the valve core 4's ejector pin 402 remains in contact with the piston rod 20, and the valve core 4 moves closer to the valve 14 under the push of the coil spring 6; the closer the valve core 4 is to the valve 14, the less compressed air flows from the intake chamber 11 into the exhaust passage 18; the valve core 4... When valve stem 401 contacts valve 14, the flow rate of compressed air from intake chamber 11 into outlet passage 18 reaches its minimum value; after piston rod 20 contacts valve core 3's ejector pin 302, piston rod 20 pushes valve core 3, causing valve stem 301 of valve core 3 to move away from valve 13, and compressed air flows from intake chamber 10 into outlet passage 16; the greater the distance between valve core 3 and valve 13, the more compressed air flows into outlet passage 16;

[0056] Reducing the amount of regulating air inside regulating chamber 2 10 decreases the pressure inside chamber 2 10, causing piston rod 20 to move closer to intake chamber 2 10; valve core 3's ejector pin 302 remains in contact with piston rod 20, and valve core 3 moves closer to valve 13 under the push of coil spring 5; the closer valve stop 301 is to valve 13, the less compressed air flows from intake chamber 10 into exhaust passage 16; when valve stop 301 is closer to valve 13... When contact occurs, the amount of compressed air flowing from the intake chamber 10 into the exhaust passage 16 reaches a minimum. After the valve core 4's ejector pin 402 contacts the piston rod 20, the valve core 4 is pushed by the piston rod 20, causing the valve stop 401 of the valve core 4 to move away from the valve, and the compressed air flows from the intake chamber 11 into the exhaust passage 18. The greater the distance between the valve stop 401 of the valve core 4 and the valve 14, the more compressed air flows into the exhaust passage 18.

[0057] The above-described motion process can be summarized as follows: Gradually increasing the amount of regulating air inside regulating chamber 2 10 causes a gradual increase in pressure within chamber 2 10, a gradual increase in the output airflow rate of outlet 16 to its maximum value, and a gradual decrease in the output airflow rate of outlet 2 18 to its minimum value; conversely, gradually decreasing the amount of regulating air inside regulating chamber 2 10 causes a gradual decrease in pressure within chamber 2 10, a gradual increase in the output airflow rate of outlet 2 18 to its maximum value, and a gradual decrease in the output airflow rate of outlet 16 to its minimum value. Therefore, this embodiment can simultaneously control the output of two compressed air streams through the movement of a single dual-diaphragm assembly.

[0058] Although the embodiments of this utility model have been disclosed above, they are not limited to the applications listed in the specification and embodiments. They can be applied to various fields suitable for this utility model. For those skilled in the art, and for those of ordinary skill in the art, various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principles and spirit of this utility model. Therefore, without departing from the general concept defined by the claims and their equivalents, this utility model is not limited to the specific details.

Claims

1. A double-acting diaphragm flow amplifier, characterized in that: Includes body (1), double diaphragm assembly (2), valve core one (3), valve core two (4), coil spring one (5), coil spring two (6); The body (1) is provided with 6 chambers: regulating chamber 1 (7), air inlet chamber 1 (8), air outlet chamber 1 (9), regulating chamber 2 (10), air inlet chamber 2 (11), and air outlet chamber 2 (12); air inlet chamber 1 (8) and air outlet chamber 1 (9) are connected by a through hole, which is called valve 1 (13); air inlet chamber 2 (11) and air outlet chamber 2 (12) are connected by a through hole, which is called valve 2 (14). The body (1) is provided with 5 pipes: air inlet 1 (15), air outlet 1 (16), air inlet 2 (17), air outlet 2 (18), and IP air inlet (19). One end of the intake duct (15) is connected to the intake chamber (8), and the other end of the intake duct (15) is connected to the outside. Compressed air from the outside flows into the intake chamber (8) through the intake duct (15); one end of the exhaust duct (16) is connected to the exhaust chamber (9), and the other end of the exhaust duct (16) is connected to the outside. Compressed air from the exhaust chamber (9) flows out to the outside through the exhaust duct (16); One end of the second intake duct (17) is connected to the second intake chamber (11), and the other end of the second intake duct (17) is connected to the outside. Compressed air from the outside flows into the second intake chamber (11) through the second intake duct (17); one end of the second exhaust duct (18) is connected to the second exhaust chamber (12), and the other end of the second exhaust duct (18) is connected to the outside. Compressed air from the second exhaust chamber (12) flows out to the outside through the second exhaust duct (18); One end of the IP air intake (19) is connected to the second regulating chamber (10), and the other end of the second air intake (17) is connected to the outside. Compressed air from the outside flows into the second regulating chamber (10) from the IP air intake (19). The compressed air flowing into intake duct 1 (15) and intake duct 2 (17) is called input air, the compressed air flowing into IP intake duct (19) is called regulating air, and the compressed air flowing out of exhaust duct 1 (16) and exhaust duct 2 (18) is called output air. The cross-sectional view of the valve core (3) is a T-shaped structure. The valve core (3) can be obtained by rotating the T-shaped structure around its own axis of symmetry. The larger diameter top of the valve core (3) is called the valve stop, and the rod-shaped part with a smaller diameter is called the ejector pin. The valve core (3) is located between the intake chamber (8) and the exhaust chamber (9). The ejector pin passes through the valve (13), and the central axis of the ejector pin coincides with the central axis of the valve (13). The valve core (3) can move linearly along the central axis of the valve (13). The helical spring (5) is located inside the exhaust chamber (9) and pushes the valve core (3) towards the intake chamber (8), so that the valve stop is pressed against the valve (13). When the valve stop is in the valve (13), the intake chamber (8) and the exhaust chamber (9) are not connected, and compressed air cannot flow from the intake chamber (8) to the exhaust chamber (9). The structure of valve core 2 (4) is the same as that of valve core 1 (3), including valve stop and ejector pin; valve core 2 (4) is located between intake chamber 2 (11) and exhaust chamber 2 (12), ejector pin passes through valve core 2 (14), and the central axis of ejector pin coincides with the central axis of valve core 2 (14); valve core 2 (4) can move linearly along the central axis of valve core 2 (14); the helical spring 2 (6) is located inside exhaust chamber 2 (12), pushing valve core 2 (4) towards intake chamber 2 (11), so that valve stop is pressed against valve core 2 (14); when valve stop is in valve core 2 (14), intake chamber 2 (11) and exhaust chamber 2 (12) are not connected, and compressed air cannot flow from intake chamber 2 (11) to exhaust chamber 2 (12); The central axis of valve one (13) coincides with the central axis of valve two (14); The dual diaphragm assembly (2) includes a piston rod (20), a flexible diaphragm one (21), a flexible diaphragm two (22), a flexible diaphragm three (23), and a flexible diaphragm four (24); the piston rod (20) is a round rod structure, and the central axis of the piston rod (20) coincides with the central axis of the valve one (13); the flexible diaphragm one (21), the flexible diaphragm two (22), the flexible diaphragm three (23), and the flexible diaphragm four (24) are all thin sheet structures and are all fixed on the piston rod (20), and the thickness direction of the four is parallel to the central axis of the piston rod (20); The dual diaphragm assembly (2) is positioned between valve one (13) and valve two (14), and the central axis of the piston rod (20) coincides with the central axis of valve one (13); the flexible diaphragm four (24) is fixed on the body (1) and together with the body (1) forms the intake chamber two (11); the flexible diaphragm three (23) is fixed on the body (1) and together with the body (1) forms the adjustment chamber two (10); the flexible diaphragm two (22) is fixed on the body (1) and together with the flexible diaphragm three (23) forms the adjustment chamber two (10). Together they form an adjustment chamber (7); the flexible diaphragm (21) is fixed on the body (1) and together with the body (1) forms an air intake chamber (8); when observed along the central axis of the piston rod (20), the arrangement order of the above mechanisms is: air outlet chamber (9), valve core (3), air intake chamber (8), flexible diaphragm (21), flexible diaphragm (22), flexible diaphragm (3) and flexible diaphragm (4) (24), air intake chamber (11), valve core (4), air outlet chamber (12); After the regulating air flows into the regulating chamber two (10) from the IP intake passage (19), the pressure inside the regulating chamber two (10) increases, the flexible diaphragm three (23) deforms and pushes the piston rod (20) towards the intake chamber one (8); the pin of the valve core two (4) remains in contact with the piston rod (20), and the valve core two (4) moves closer to the valve two (14) under the push of the coil spring two (6); the closer the valve core two (4) is to the valve two (14), the less compressed air flows from the intake chamber two (11) into the exhaust passage two (18); the valve When the valve stop of valve core 2 (4) comes into contact with valve 2 (14), the flow rate of compressed air from intake chamber 2 (11) into exhaust passage 2 (18) reaches the minimum value; after the piston rod (20) comes into contact with the pin of valve core 1 (3), the piston rod (20) pushes valve core 1 (3), causing the valve stop of valve core 1 (3) to move away from valve 1 (13), and compressed air flows from intake chamber 1 (8) into exhaust passage 1 (16); the greater the distance between valve core 1 (3) and valve 1 (13), the more compressed air flows into exhaust passage 1 (16); Reducing the amount of regulating air inside regulating chamber two (10) decreases the pressure inside regulating chamber two (10), causing the piston rod (20) to move closer to the intake chamber two (11); the valve core one (3) remains in contact with the piston rod (20), and the valve core one (3) moves closer to the valve one (13) under the push of the coil spring one (5); the closer the valve stop is to the valve one (13), the less compressed air flows from the intake chamber one (8) into the exhaust passage one (16); when the valve stop is closer to the valve one (13), the less compressed air flows from the intake chamber one (8) into the exhaust passage one (16). 3) When contact occurs, the amount of compressed air flowing from intake chamber 1 (8) into exhaust passage 1 (16) reaches a minimum; after the pin of valve core 2 (4) contacts the piston rod (20), valve core 2 (4) is pushed by the piston rod (20), causing the valve stop of valve core 2 (4) to move away from valve 1, and compressed air flows from intake chamber 2 (11) into exhaust passage 2 (18); the farther the distance between the valve stop of valve core 2 (4) and valve 2 (14) is, the more compressed air flows into exhaust passage 2 (18).

2. The double-acting diaphragm flow amplifier according to claim 1, characterized in that, The air outlet (16) and the regulating chamber (7) are connected.

3. The double-acting diaphragm flow amplifier according to claim 1, characterized in that: The flexible diaphragm one (21), the flexible diaphragm two (22), and the body (1) form a cavity called the exhaust cavity (25); the exhaust cavity (25) is connected to the outside. The piston rod (20) is a hollow cylindrical structure and has a through hole, called the exhaust hole (26); the central axis of the exhaust hole (26) is perpendicular to the central axis of the piston rod (20), and the exhaust hole (26) is located inside the exhaust chamber (25).

4. The double-acting diaphragm flow amplifier according to claim 1, characterized in that: The air intake chamber 1 (8) is equipped with a helical spring 3 (27); one end of the helical spring 3 (27) is in contact with the body (1), and the other end is in contact with the piston rod (20), and applies a thrust to the piston rod (20) pointing towards the air intake chamber 2 (11); The second air intake chamber (11) is equipped with a fourth helical spring (28); one end of the fourth helical spring (28) is in contact with the body (1), and the other end is in contact with the piston rod (20), and applies a thrust to the piston rod (20) pointing towards the first air intake chamber (8).

5. A double-acting diaphragm flow amplifier according to claim 4, characterized in that: The air intake duct (15) is provided with an adjusting bolt (29); by rotating the adjusting bolt (29), the cross-sectional area of ​​the air intake duct (15) will change. The second air intake (17) is provided with an adjusting bolt (30); by rotating the adjusting bolt (30), the cross-sectional area of ​​the second air intake (17) will change.

6. A double-acting diaphragm flow amplifier according to claim 1, characterized in that: The air outlet chamber 1 (9) is provided with an adjusting bolt 3 (31); one end of the helical spring 1 (5) is in contact with the adjusting bolt 3 (31), and the other end is in contact with the valve core 1 (3); rotating the adjusting bolt 3 (31) will change the thrust applied by the helical spring 1 (5) to the valve core 1 (3); The second air outlet chamber (12) is equipped with an adjusting bolt four (32); one end of the second helical spring (6) is in contact with the adjusting bolt four (32), and the other end is in contact with the valve core two (4); rotating the adjusting bolt four (32) will change the thrust applied by the helical spring two (6) to the valve core two (4).

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