Automatic proportional integral pressure controller

Abstract

The present invention discloses an automatic proportional-integral pressure controller, which drives the rotation of a floating plate based on the pressure difference between the actual pressure in the air chamber and the preset pressure, and converts the rotation of the floating plate into the up and down movement of the baffle to adjust the distance between the baffle and the nozzle, thereby changing the output air pressure of the pneumatic amplifier and converting the movement of the mechanical structure into air pressure changes. The output air pressure change controls the opening and closing state and opening degree of the intake valve or exhaust valve, thereby controlling the intake or exhaust of the air chamber; on the other hand, it is transmitted to the third wave spring assembly and the second wave spring assembly. Under the buffering effect of the air storage chamber, the air pressure change of the second wave spring assembly lags, and the pressure difference change between the two plays a feedback regulating role in the rotation of the floating plate. Automatic proportional-integral control of air pressure is achieved by two sets of wave spring assemblies, with fast response speed and high control accuracy. It adopts a purely mechanical structure design with strong anti-interference ability, and the overall structure is simple and easy to assemble and operate.

Description

Technical Field

[0001] The present invention relates to the technical field of automatic air pressure controllers, in particular to an automatic proportional integral pressure controller. Background Art

[0002] In underground construction, slurry and earth pressure shield machines are widely used. As a key system, the pressure maintenance system is directly related to construction safety and progress. Due to the complex and changing excavation environment during construction, the shield machine's air chamber must maintain stable air pressure. The automatic air pressure controller plays a key role in maintaining this pressure and is the core component of the pressure maintenance system. The automatic air pressure controller collects air chamber pressure and compares it with a manually set pressure. It then automatically calculates and outputs a control signal to control the opening and closing of the air chamber's inlet and exhaust valves, thereby controlling the air chamber pressure to maintain consistency with the set pressure. However, most existing automatic air pressure controllers are electronically controlled, requiring conversion between pressure and electrical signals. These controllers are susceptible to electromagnetic interference and have low reliability. Furthermore, while some purely mechanical pneumatic pressure controllers exist, they have numerous parts, complex structures, and cumbersome assembly. Furthermore, they suffer from low adjustment precision in terms of response speed, control accuracy, and initial output pressure. Summary of the Invention

[0003] The present invention provides an automatic proportional-integral pressure controller to solve the technical problems that the existing electronically controlled pressure controller is susceptible to electromagnetic interference and has low reliability, and the existing pneumatic pressure controller has a complex structure and cumbersome assembly.

[0004] According to one aspect of the present invention, an automatic proportional-integral pressure controller is provided, comprising a fixed plate, a floating plate, an elastic mechanism, a first wave spring assembly, a second wave spring assembly, a third wave spring assembly, a fourth wave spring assembly, a first connecting block, a baffle, a nozzle, a pneumatic amplifier, and an air storage chamber. The fixed plate is fixedly arranged, the floating plate is located above the fixed plate, and the middle parts of the two are connected by the elastic mechanism. The first wave spring assembly and the fourth wave spring assembly, the second wave spring assembly and the third wave spring assembly are symmetrically arranged on both sides of the elastic mechanism. The two ends of the four wave spring assemblies are respectively connected to the fixed plate and the floating plate. Each wave spring assembly generates a telescopic displacement according to the change of the input air pressure to generate an upward thrust or a downward pull on the floating plate. The baffle is connected to the floating plate through the first connecting block. The nozzle is mounted on the fixed plate, and the baffle is located directly below the nozzle. The input chamber and air source chamber of the pneumatic amplifier and the nozzle are all connected to the first air source. The output chamber of the pneumatic amplifier is connected to the air inlet and air storage chamber of the second wave spring assembly. The air storage chamber is connected to the air inlet of the third wave spring assembly. The output chamber is also connected to the air inlet pneumatic regulating valve and the exhaust pneumatic regulating valve of the air storage through the output port, so as to control the opening and closing and the opening degree of the air inlet pneumatic regulating valve and the exhaust pneumatic regulating valve. The air inlet of the fourth wave spring assembly is connected to the second air source, and the pressure value output by the second air source is obtained by linearly reducing the preset air storage pressure value. The air inlet of the first wave spring assembly is connected to the air storage through the receiving port, and a pneumatic pressure transmitter is provided between the receiving port and the air storage for linearly reducing the actual pressure value of the air storage, and the linear function is the same as that of the second air source.

[0005] When the actual pressure value of the air chamber is not equal to the preset pressure value, the expansion and contraction amplitudes of the first wave spring assembly and the fourth wave spring assembly are different, thereby driving the floating plate to rotate, and then adjusting the distance between the baffle and the nozzle, so that the input pressure and output pressure of the pneumatic amplifier change, thereby controlling the expansion and contraction amplitudes of the second wave spring assembly and the third wave spring assembly to change, so as to adjust the rotation amplitude of the floating plate, and at the same time control the opening and closing state and opening degree of the intake pneumatic regulating valve or the exhaust pneumatic regulating valve to control the air intake or exhaust of the air chamber until the actual pressure value of the air chamber is equal to the preset pressure value. In the automatic control process of the air chamber pressure, the first wave spring assembly and the fourth wave spring assembly play a proportional control role, and the second wave spring assembly and the third wave spring assembly play an integral control role.

[0006] Furthermore, the second wave spring assembly and the third wave spring assembly are arranged on the inner side, and the first wave spring assembly and the fourth wave spring assembly are arranged on the outer side, so as to enhance the proportional control effect and weaken the integral control effect;

[0007] Alternatively, the second wave spring assembly and the third wave spring assembly are arranged on the outside, and the first wave spring assembly and the fourth wave spring assembly are arranged on the inside, so as to enhance the integral control effect and weaken the proportional control effect.

[0008] Furthermore, transverse movable grooves and limiting grooves are provided on the fixed plate and the floating plate, and protrusions are provided at both ends of each wave spring assembly. The protrusions at both ends of each wave spring assembly slide with the movable grooves on the fixed plate and the floating plate respectively, and the two ends of each wave spring assembly are fixed in the limiting grooves of the fixed plate and the floating plate by screws. When the size or stiffness of the four wave spring assemblies deviates due to manufacturing errors, which leads to unbalanced force on the floating plate, the floating plate can be adjusted to a force balanced state by loosening the fixing screws at both ends and fine-tuning the fixed position of the wave spring assembly.

[0009] Furthermore, the nozzle is mounted on the fixed plate through a second connecting block, a vertical limiting groove is provided on the second connecting block, and a screw passes through the vertical limiting groove to fix the second connecting block to the fixed plate. By adjusting the position of the screw in the limiting groove, the initial distance between the nozzle and the baffle can be roughly adjusted.

[0010] Furthermore, the installation position of the first connecting block on the floating plate can be adjusted left and right.

[0011] Furthermore, two threaded holes are provided on the first connecting block, and one end of the baffle is fixedly mounted on the first connecting block by a screw cooperating with one of the threaded holes, and another screw passes through the other threaded hole from below and presses upward against the lower surface of the baffle, and the initial distance between the baffle and the nozzle can be fine-tuned by adjusting the protruding length of the other screw.

[0012] Furthermore, the elastic mechanism includes an upper support seat, an upper support plate, a horizontal elastic plate, a vertical elastic plate, a lower support plate and a lower support seat, the upper support seat is connected to the floating plate, the lower support seat is connected to the fixed plate, the upper support plate is installed on the upper support seat, and the lower support plate is installed on the lower support seat, the horizontal elastic plate and the vertical elastic plate are respectively connected to the upper support plate and the lower support plate, when the floating plate rotates, the horizontal elastic plate and the vertical elastic plate are elastically deformed and generate a torque in the opposite direction, so that the floating plate returns to its original state when no force is applied.

[0013] Furthermore, the restoring torque of the elastic mechanism is adjusted by adjusting the thickness of the horizontal elastic piece and the vertical elastic piece.

[0014] Furthermore, a throttle valve is provided between the air storage chamber and the output chamber of the pneumatic amplifier.

[0015] Furthermore, the wave spring assembly includes an upper cover plate, a wave spring and a lower cover plate, the upper end of the upper cover plate is connected to the floating plate, the lower end of the lower cover plate is connected to the fixed plate, the two ends of the wave spring are respectively connected to the upper cover plate and the lower cover plate, and an air inlet is provided on the lower cover plate for communicating with an external air source, the air inlet is connected to the air inlet of the wave spring, and when the external air source inputs air pressure into the wave spring, the wave spring extends upward to push the floating plate to rotate.

[0016] The present invention has the following effects:

[0017] The automatic proportional-integral pressure controller of the present invention achieves different extensions of the first and fourth wave spring assemblies based on the pressure difference between the actual pressure in the air chamber and the preset pressure, thereby driving the rotation of the floating plate. The rotation of the floating plate is converted into the up and down movement of the baffle to adjust the distance between the baffle and the nozzle, thereby changing the output air pressure of the pneumatic amplifier, converting the movement of the mechanical structure into air pressure changes. The change in the output air pressure of the pneumatic amplifier can control the opening and closing state and opening degree of the air intake or exhaust pneumatic control valve, thereby controlling the air intake or exhaust of the air chamber and, in turn, the air chamber pressure. The output air pressure of the pneumatic amplifier is directly transmitted to the third wave spring assembly and, at the same time, is transmitted to the second wave spring assembly through the air storage chamber. Due to the buffering effect of the air storage chamber, the air pressure change of the second wave spring assembly lags behind that of the third wave spring assembly. The pressure difference between the second and third wave spring assemblies provides feedback regulation for the rotation of the floating plate. During the automatic control of the gas tank pressure, the first and fourth wave spring assemblies directly control the rotation amplitude of the floating plate, providing proportional control, while the second and third wave spring assemblies provide feedback control of the floating plate's rotation amplitude, providing integral control. The automatic proportional-integral pressure controller of the present invention achieves automatic proportional-integral control of gas pressure through two sets of wave spring assemblies, offering fast response, high control accuracy, and excellent stability. Its purely mechanical design offers strong anti-interference capabilities, simple overall structure, and easy assembly and operation.

[0018] In addition to the above-described objects, features and advantages, the present invention has other objects, features and advantages. The present invention will be further described in detail below with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] The accompanying drawings, which constitute part of this application, are intended to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are intended to explain the present invention and do not constitute an undue limitation of the present invention. In the accompanying drawings:

[0020] Figure 1 It is a schematic diagram of the principle of the automatic proportional integral pressure controller of the preferred embodiment of the present invention.

[0021] Figure 2 It is a schematic structural diagram of the mechanical structure of the automatic proportional integral pressure controller according to a preferred embodiment of the present invention when the floating plate is not rotating.

[0022] Figure 3 It is a schematic structural diagram of the mechanical structure of the automatic proportional-integral pressure controller according to a preferred embodiment of the present invention after the floating plate rotates clockwise.

[0023] Figure 4 It is a schematic diagram of the exploded structure of the mechanical structure part of the automatic proportional integral pressure controller according to the preferred embodiment of the present invention.

[0024] Figure 5 It is a schematic diagram of the exploded structure in which the baffle is installed on the first connecting block in a preferred embodiment of the present invention.

[0025] Figure 6 It is a schematic diagram of the exploded structure of the elastic mechanism of the preferred embodiment of the present invention.

[0026] Figure 7 It is a schematic cross-sectional structure diagram of a wave spring assembly according to a preferred embodiment of the present invention.

[0027] Description of Reference Numerals

[0028] 1. Fixed plate; 2. Floating plate; 3. Elastic mechanism; 4. First wave spring assembly; 5. Second wave spring assembly; 6. Third wave spring assembly; 7. Fourth wave spring assembly; 8. First connecting block; 9. Baffle; 10. Nozzle; 11. Second connecting block; 12. Pneumatic amplifier; 13. Orifice; 14. Throttle valve; 15. Air storage chamber; 16. Receiving port; 17. Second air source; 18. Output port; 19. First air source; 20. Inlet Pneumatic regulating valve; 21. Exhaust pneumatic regulating valve; 22. Air chamber; 23. Pneumatic pressure transmitter; 121. Input chamber; 122. Output chamber; 123. Air source chamber; 31. Upper support seat; 32. Upper support plate; 33. Horizontal elastic plate; 34. Vertical elastic plate; 35. Lower support plate; 36. Lower support seat; 41. Upper cover plate; 42. Wave spring; 43. Lower cover plate; 431. Air inlet; 91. First screw; 92. Second screw. DETAILED DESCRIPTION

[0029] The embodiments of the present invention are described in detail below with reference to the accompanying drawings. However, the present invention can be implemented in many different ways as defined and covered below.

[0030] like Figure 1 As shown, a preferred embodiment of the present invention provides an automatic proportional-integral pressure controller, comprising a fixed plate 1, a floating plate 2, an elastic mechanism 3, a first wave spring assembly 4, a second wave spring assembly 5, a third wave spring assembly 6, a fourth wave spring assembly 7, a first connecting block 8, a baffle 9, a nozzle 10, a pneumatic amplifier 12, and an air storage chamber 15. The fixed plate 1 is fixedly disposed, and the floating plate 2 is located above the fixed plate 1, with the middle portion of the two being connected by the elastic mechanism 3. Specifically, the fixed plate 1 and the floating plate 2 are disposed parallel to each other, the lower end of the elastic mechanism 3 is fixedly connected to the middle portion of the fixed plate 1, and the upper end of the elastic mechanism 3 is fixedly connected to the middle portion of the floating plate 2. The floating plate 2 rotates slightly about the connection point W between the elastic mechanism 3 and the fixed plate 1. When the floating plate 2 rotates, the elastic mechanism 3 twists around the fulcrum W and generates a restoring torque, thereby driving the floating plate 2 back to its original position when the forces on the floating plate 2 are balanced. The first wave spring assembly 4 and the fourth wave spring assembly 7, the second wave spring assembly 5 and the third wave spring assembly 6 are symmetrically arranged on both sides of the elastic mechanism 3. The two ends of the four wave spring assemblies are respectively connected to the fixed plate 1 and the floating plate 2. Each wave spring assembly can generate telescopic displacement according to the change of the input air pressure to generate an upward thrust or downward pull on the floating plate 2. Among them, the telescopic displacement of the wave spring assembly is in a certain relationship with the input air pressure. The greater the input air pressure, the greater the extension. When the force applied to the floating plate 2 by the wave spring assemblies on both sides of the elastic mechanism 3 is unbalanced, the floating plate 2 will rotate clockwise or counterclockwise around the fulcrum W. The baffle 9 is connected to the floating plate 2 through the first connecting block 8. The nozzle 10 is installed on the fixed plate 1, and the baffle 9 is located directly below the nozzle 10. When the floating plate 2 rotates around the fulcrum W, the baffle 9 will move up and down with the rotation of the floating plate 2, thereby adjusting the distance between the baffle 9 and the nozzle 10. For example, in the initial state, as Figure 2 As shown, the floating plate 2 does not rotate, the floating plate 2 and the fixed plate 1 remain parallel, and the distance between the baffle 9 and the nozzle 10 is the initial distance; in the working state, as shown Figure 3As shown, the floating plate 2 rotates clockwise, driving the first connecting block 8 and baffle 9 downward, increasing the distance between the baffle 9 and the nozzle 10. The input chamber 121 and air source chamber 123 of the pneumatic amplifier 12, as well as the nozzle 10, are all connected to the first air source 19. Optionally, a throttle orifice 13 is provided on the pipeline connecting the first air source 19, the nozzle 10, and the input chamber 121 of the pneumatic amplifier 12. The output chamber 122 of the pneumatic amplifier 12 is connected to the air inlet of the second wave spring assembly 5 and the air storage chamber 15. The air storage chamber 15 is connected to the air inlet of the third wave spring assembly 6. The output chamber 122 is also connected to the air intake pneumatic control valve 20 and the exhaust pneumatic control valve 21 of the air reservoir 22 via the output port 18, for controlling the opening and closing of the air intake pneumatic control valve 20 and the exhaust pneumatic control valve 21. Preferably, a throttle valve 14 is provided between the air storage chamber 15 and the output chamber 122 of the pneumatic amplifier 12. The opening of the throttle valve 14 is adjustable, thereby adjusting the throttling effect. When the distance between the baffle 9 and the nozzle 10 changes, the gas flow resistance at the nozzle 10 outlet changes, thereby changing the input pressure of the pneumatic amplifier 12 and, in turn, the output pressure of the pneumatic amplifier 12. When the output pressure of the pneumatic amplifier 12 changes, the air pressure of the third wave spring assembly 6 lags behind that of the second wave spring assembly 5 because the output chamber 122 is directly connected to the air inlet of the second wave spring assembly 5, while the air inlet of the third wave spring assembly 6 is connected to the output chamber 122 through the air storage chamber 15. Furthermore, the air pressure output from the output chamber 122 is connected to the intake pneumatic control valve 20 and the exhaust pneumatic control valve 21 via the output port 18. When the output air pressure of the output chamber 122 changes, the opening and closing states and opening degrees of the intake and exhaust pneumatic control valves 20 and 21 can be controlled. The air inlet of the fourth wave spring assembly 7 is connected to a second air source 17. The pressure output by the second air source 17 is linearly scaled down based on the preset air chamber pressure. The air inlet of the first wave spring assembly 4 is connected to the air chamber 22 via a receiving port 16. A pneumatic pressure transmitter 23 is provided between the receiving port 16 and the air chamber 22, which is used to linearly scale down the actual pressure in the air chamber 22 using the same linear function as the second air source 17. When the air pressures input to the first and fourth wave spring assemblies 4 and 7 differ, their elongations differ, thereby driving the floating plate 2 to rotate about the fulcrum W.

[0031] When the actual pressure value of the air storage 22 is not equal to the preset pressure value, the expansion and contraction amplitudes of the first wave spring assembly 4 and the fourth wave spring assembly 7 are different, thereby driving the floating plate 2 to rotate, and then adjusting the distance between the baffle 9 and the nozzle 10, so that the input pressure and output pressure of the pneumatic amplifier 12 change, thereby controlling the expansion and contraction amplitudes of the second wave spring assembly 5 and the third wave spring assembly 6 to change, so as to adjust the rotation amplitude of the floating plate 2, and at the same time control the opening and closing state and opening degree of the intake pneumatic regulating valve 20 or the exhaust pneumatic regulating valve 21 to control the intake or exhaust of the air storage 22 until the actual pressure value of the air storage 22 is equal to the preset pressure value. In the automatic control process of the air storage pressure, the first wave spring assembly 4 and the fourth wave spring assembly 7 play a proportional control role, and the second wave spring assembly 5 and the third wave spring assembly 6 play an integral control role.

[0032] It can be understood that the automatic proportional-integral pressure controller of this embodiment achieves different extensions of the first and fourth wave spring assemblies 4 and 7 based on the pressure difference between the actual pressure in the air reservoir 22 and the preset pressure, thereby driving the rotation of the floating plate 2. This rotation of the floating plate 2 is converted into the up and down movement of the baffle 9 to adjust the distance between the baffle 9 and the nozzle 10, thereby changing the output air pressure of the pneumatic amplifier 12, thus converting the movement of the mechanical structure into air pressure fluctuations. The output air pressure changes of the pneumatic amplifier 12 can, on the one hand, control the opening and closing state of the air intake pneumatic control valve 20 or the air exhaust pneumatic control valve 21, thereby controlling the air intake or exhaust of the air reservoir 22 and, in turn, the pressure in the air reservoir 22. On the other hand, the output air pressure of the pneumatic amplifier 12 is directly transmitted to the second wave spring assembly 5 and, simultaneously, to the third wave spring assembly 6 through the air storage chamber 15. Due to the buffering effect of the air storage chamber 15, the air pressure changes of the third wave spring assembly 6 lag behind that of the second wave spring assembly 5. The pressure difference between the second and third wave spring assemblies 5 and 6 provides feedback regulation for the rotation of the floating plate 2. During the automatic control of the gas tank pressure, the first and fourth wave spring assemblies 4 and 7 directly control the rotation amplitude of the floating plate 2, providing proportional control, while the second and third wave spring assemblies 5 and 6 provide feedback control of the rotation amplitude of the floating plate 2, providing integral control. The automatic proportional-integral pressure controller of the present invention achieves automatic proportional-integral control of gas pressure through two sets of wave spring assemblies, offering fast response, high control accuracy, and excellent stability. Its purely mechanical design offers strong anti-interference capabilities, simple overall structure, and easy assembly and operation.

[0033] It can be understood that the second wave spring assembly 5 and the third wave spring assembly 6 are arranged on the inner side, and the first wave spring assembly 4 and the fourth wave spring assembly 7 are arranged on the outer side, so as to enhance the proportional control effect and weaken the integral control effect. Alternatively, the second wave spring assembly 5 and the third wave spring assembly 6 are arranged on the outer side, and the first wave spring assembly 4 and the fourth wave spring assembly 7 are arranged on the inner side, so as to enhance the integral control effect and weaken the proportional control effect.

[0034] Among them, when the second wave spring assembly 5 and the third wave spring assembly 6 are arranged close to the elastic mechanism 3, and the first wave spring assembly 4 and the fourth wave spring assembly 7 are arranged away from the elastic mechanism 3, the first wave spring assembly 4 and the fourth wave spring assembly 7 are farther from the fulcrum W, and the applied torque is larger, while the second wave spring assembly 5 and the third wave spring assembly 6 are closer to the fulcrum W and the applied torque is smaller, thereby enhancing the proportional control effect and weakening the integral control effect. When the second wave spring assembly 5 and the third wave spring assembly 6 are arranged away from the elastic mechanism 3, and the first wave spring assembly 4 and the fourth wave spring assembly 7 are arranged close to the elastic mechanism 3, the first wave spring assembly 4 and the fourth wave spring assembly 7 are closer to the fulcrum W and the applied torque is smaller, while the second wave spring assembly 5 and the third wave spring assembly 6 are farther from the fulcrum W and the applied torque is larger, thereby weakening the proportional control effect and enhancing the integral control effect.

[0035] In addition, the positions of the first wave spring assembly 4 and the fourth wave spring assembly 7 can be swapped. After the position swap, the control mode is a reaction type, and the intake pneumatic regulating valve 20 and the exhaust pneumatic regulating valve 21 correspondingly adopt reaction type response valves.

[0036] It is understandable that Figure 4 As shown, the fixed plate 1 and the floating plate 2 are provided with transverse moving grooves and limiting grooves, and each wave spring assembly is provided with protrusions at both ends. The protrusions at both ends of each wave spring assembly slide in conjunction with the moving grooves on the fixed plate 1 and the floating plate 2, respectively, and the two ends of each wave spring assembly are fixed to the limiting grooves of the fixed plate 1 and the floating plate 2 by screws. Ideally, the four wave spring assemblies have the same size and stiffness, so a symmetrical distribution is adopted to balance the force on the floating plate 2. However, when the size or stiffness of the four wave spring assemblies deviate due to manufacturing errors, resulting in an unbalanced force on the floating plate 2, the floating plate 2 can be adjusted to a force-balanced state by loosening the fixing screws at both ends and fine-tuning the fixed position of the wave spring assembly, thereby improving the air pressure control accuracy of the controller.

[0037] Optionally, two protrusions are provided at each end of the wave spring assembly, and four movable grooves are provided on the upper surface of the fixed plate 1 and the lower surface of the floating plate 2. The two protrusions at both ends of the first wave spring assembly 4 and the second wave spring assembly 5 are located in the two movable grooves on the left side of the fulcrum W, and the two protrusions at both ends of the third wave spring assembly 6 and the fourth wave spring assembly 7 are located in the two movable grooves on the right side of the fulcrum W. At the same time, two limiting grooves running through the upper and lower parts are also provided on the fixed plate 1 and the floating plate 2, one is located on the left side of the fulcrum W, and the other is located on the right side of the fulcrum W. The limiting groove on the left is used to fix the first wave spring assembly 4 and the second wave spring assembly 5, and the limiting groove on the right is used to fix the third wave spring assembly 6 and the fourth wave spring assembly 7.

[0038] In addition, the nozzle 10 is mounted on the fixing plate 1 via a second connecting block 11. A vertical retaining groove is defined in the second connecting block 11, through which a screw passes to secure the second connecting block 11 to the fixing plate 1. By adjusting the position of the screw in the retaining groove, the initial distance between the nozzle 10 and the baffle 9 can be roughly adjusted, thereby roughly adjusting the initial output pressure of the controller, i.e., the pressure output to the intake and exhaust valves. The nozzle 10 is fixedly mounted on the second connecting block 11 via a threaded connection.

[0039] Furthermore, the mounting position of the first connecting block 8 on the floating plate 2 can be adjusted left and right, thereby facilitating adjustment of the horizontal distance between the first connecting block 8 and the baffle 9 and the fulcrum W. Different distances from the fulcrum W result in different response speeds and control accuracy for the vertical movement of the first connecting block 8 and the baffle 9 in response to the rotation of the floating plate 2. Therefore, by adjusting the mounting position of the first connecting block 8 on the floating plate 2, the response speed and control accuracy of the controller can be altered, making adjustment very convenient. Specifically, a positioning hole is defined at the top of the first connecting block 8, and a transverse positioning slot is defined on the floating plate 2. Screws or bolts pass through the positioning slot and engage with the positioning hole, thereby securing the first connecting block 8 to the floating plate 2. Loosening the screws or bolts allows the first connecting block 2 to move laterally. Once adjusted into position, the screws or bolts are tightened, resulting in a very convenient operation.

[0040] In addition, if Figure 5As shown, the first connecting block 8 has two threaded holes, and one end of the baffle 9 is fixedly mounted on the first connecting block 8 by a screw engaging with one of the threaded holes. Another screw passes through the other threaded hole from below and presses upward against the lower surface of the baffle 9. By adjusting the extension length of the other screw, the initial distance between the baffle 9 and the nozzle 10 can be fine-tuned. Specifically, a through hole is provided on one end of the baffle 9, and the first connecting block 8 has two threaded holes. One end of the baffle 9 is fixedly mounted on the first connecting block 8 by a first screw 91 passing through the through hole and engaging with one of the threaded holes. A second screw 92 passes through the other threaded hole from below the first connecting block 8 and presses upward against the lower surface of the baffle 9. By twisting the second screw 92, its extension can be adjusted, thereby adjusting the upward displacement of the baffle 9, thereby finely adjusting the initial distance between the baffle 9 and the nozzle 10, and accurately adjusting the initial output pressure of the controller, further improving the air pressure control accuracy.

[0041] It is understandable that Figure 6 As shown, the elastic mechanism 3 includes an upper support seat 31, an upper support piece 32, a horizontal elastic piece 33, a vertical elastic piece 34, a lower support piece 35, and a lower support seat 36. The upper support seat 31 is connected to the floating plate 2, and the lower support seat 36 is connected to the fixed plate 1. The upper support piece 32 is mounted on the upper support seat 31, and the lower support piece 35 is mounted on the lower support seat 36. The horizontal elastic piece 33 and the vertical elastic piece 34 are respectively connected to the upper support piece 32 and the lower support piece 35. When the floating plate 2 rotates, the horizontal elastic piece 33 and the vertical elastic piece 34 undergo elastic deformation and generate a reverse torque, so that the floating plate 2 can return to its original shape when no force is applied. The restoring torque of the elastic mechanism 3 can be adjusted by adjusting the thickness of the horizontal elastic piece 33 and the vertical elastic piece 34. It is understood that in other embodiments of the present invention, the elastic mechanism 3 can also adopt an elastic rod or other elastic structure.

[0042] It is understandable that Figure 7As shown, each wave spring assembly includes an upper cover plate 41, a wave spring 42, and a lower cover plate 43. The upper end of the upper cover plate 41 is connected to the floating plate 2, and the lower end of the lower cover plate 43 is connected to the fixed plate 1. The ends of the wave spring 42 are connected to the upper and lower cover plates 41 and 43, respectively. The lower cover plate 43 has an air inlet 431 for communicating with an external air source. The air inlet 431 is connected to the air inlet of the wave spring 42. When air pressure from the external air source enters the wave spring 42, the wave spring 42 extends upward to rotate the floating plate 2. The upper end of the lower cover plate 43 extends deep into the wave spring 42 to prevent excessive compression or extension. The wave spring 42 is a bellows.

[0043] It can be understood that the working process of the automatic proportional integral pressure controller of the present invention is:

[0044] When the controller is not working, there is no air pressure in the four wave spring assemblies, and the floating plate 2 is in an initial state, remaining parallel to the fixed plate 1.

[0045] After the controller is activated, when the actual pressure in air reservoir 22 is less than the preset pressure, that is, the pressure at receiving port 16 is less than the pressure provided by second air source 17, the air pressure within fourth wave spring assembly 7 is greater than the air pressure within first wave spring assembly 4, and the fourth wave spring assembly 7 extends more than the first wave spring assembly 4, thereby pushing floating plate 2 to rotate counterclockwise about fulcrum W and driving first connecting block 8 and baffle 9 upward. This reduces the distance between baffle 9 and nozzle 10, increases the input pressure of pneumatic amplifier 12, and simultaneously increases the output pressure linearly. Because the pressure in output chamber 122 flows directly into second wave spring assembly 5 and then into third wave spring assembly 6 after throttling and inflation buffering, the air pressure within third wave spring assembly 6 lags behind and becomes less than that of second wave spring assembly 5. The pressure difference between the two drives floating plate 2 to rotate clockwise, mitigating overshoot caused by the proportional effect. The pressure difference between the first and fourth wave spring assemblies 4 and 7 acts as a direct force, while the pressure difference between the second and third wave spring assemblies 5 and 6 acts as a feedback force. Under these direct and feedback forces, the floating plate 2 ultimately rotates slightly counterclockwise, slightly reducing the distance between the baffle 9 and the nozzle 10. The input pressure of the pneumatic amplifier 12 increases slightly, but after linear amplification by the pneumatic amplifier 12, the pressure at the output port 18 increases. When the output pressure of the pneumatic amplifier 12 exceeds the threshold value P2, the intake pneumatic control valve 20 is controlled to open, the exhaust pneumatic control valve 21 is closed, and the opening of the intake pneumatic control valve 20 is controlled. The air chamber 22 enters the intake state, and the pressure in the air chamber 22 gradually increases until the actual pressure equals the preset pressure. Conversely, when the actual pressure in air reservoir 22 exceeds the preset pressure—that is, the pressure at receiving port 16 exceeds the pressure provided by second air source 17—floating plate 2 eventually rotates clockwise, slightly increasing the distance between baffle 9 and nozzle 10. The input pressure to pneumatic amplifier 12 decreases slightly, but after linear amplification by pneumatic amplifier 12, its output pressure decreases significantly, reducing the pressure at output port 18. When the output pressure of pneumatic amplifier 12 falls below threshold value P2, inlet pneumatic control valve 20 is closed and exhaust pneumatic control valve 21 is opened. The opening of exhaust pneumatic control valve 21 is also controlled, placing air reservoir 22 in an exhaust state. The pressure in air reservoir 22 gradually decreases until the actual pressure equals the preset pressure. After a period of regulation, the actual pressure in air reservoir 22 finally equals the preset pressure. At this point, the output pressure of pneumatic amplifier 12 is P2. Both inlet and exhaust pneumatic control valves 20 and 21 are closed, maintaining pressure in air reservoir 22.It can be understood that in actual applications, the adjustment stroke of the intake pneumatic control valve 20 is (P2, P3), and the adjustment stroke of the exhaust pneumatic control valve 21 is (P1, P2), that is, when the input pressure is greater than P2, the intake pneumatic control valve 20 is controlled to open and its opening is adjusted. If it is less than P2, the exhaust pneumatic control valve 21 is controlled to open and its opening is adjusted, wherein 0.2bar≤P1<P2<P3≤1bar, and P2=(P1+P3) / 2.

[0046] The foregoing description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Those skilled in the art will readily appreciate that various modifications and variations of the present invention are possible. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present invention are intended to be within the scope of protection of the present invention.

Claims

1. An automatic proportional integral pressure controller, characterized in that: The invention comprises a fixed plate (1), a floating plate (2), an elastic mechanism (3), a first wave spring assembly (4), a second wave spring assembly (5), a third wave spring assembly (6), a fourth wave spring assembly (7), a first connecting block (8), a baffle (9), a nozzle (10), a pneumatic amplifier (12) and an air storage chamber (15), wherein the fixed plate (1) is fixedly arranged, the floating plate (2) is located above the fixed plate (1), and the middle part of the two is connected by the elastic mechanism (3), the first wave spring assembly (4) and the fourth wave spring assembly (7) are connected. The second wave spring assembly (5) and the third wave spring assembly (6) are symmetrically arranged on both sides of the elastic mechanism (3). The two ends of the four wave spring assemblies are respectively connected to the fixed plate (1) and the floating plate (2). Each wave spring assembly generates a telescopic displacement according to the input air pressure change to generate an upward thrust or a downward pull on the floating plate (2). The baffle (9) is connected to the floating plate (2) through the first connecting block (8). The nozzle (10) is installed on the fixed plate (1), and the baffle (9) is located between the nozzle ( 10), the input chamber (121) and the air source chamber (123) of the pneumatic amplifier (12) and the nozzle (10) are all connected to the first air source (19), the output chamber (122) of the pneumatic amplifier (12) is connected to the air inlet of the second wave spring assembly (5) and the air storage chamber (15), the air storage chamber (15) is connected to the air inlet of the third wave spring assembly (6), and the output chamber (122) is also connected to the air inlet pneumatic regulating valve (20) and the exhaust pneumatic regulating valve (21) of the air chamber (22) through the output port (18) for controlling the air inlet. The opening and closing and opening degree of the pneumatic regulating valve (20) and the exhaust pneumatic regulating valve (21) are controlled. The air inlet of the fourth wave spring assembly (7) is connected to the second air source (17). The pressure value output by the second air source (17) is obtained by linearly reducing the preset air chamber pressure value. The air inlet of the first wave spring assembly (4) is connected to the air chamber (22) through the receiving port (16). A pneumatic pressure transmitter (23) is provided between the receiving port (16) and the air chamber (22) for linearly reducing the actual pressure value of the air chamber (22). The linear function is the same as that of the second air source (17). When the actual pressure value of the air chamber (22) is not equal to the preset pressure value, the expansion and contraction amplitudes of the first wave spring assembly (4) and the fourth wave spring assembly (7) are different, thereby driving the floating plate (2) to rotate, and then adjusting the distance between the baffle (9) and the nozzle (10), so that the input pressure and output pressure of the pneumatic amplifier (12) change, thereby controlling the expansion and contraction amplitudes of the second wave spring assembly (5) and the third wave spring assembly (6) to change, so as to adjust the rotation amplitude of the floating plate (2), and at the same time control the opening and closing state and opening degree of the air intake pneumatic regulating valve (20) or the air exhaust pneumatic regulating valve (21), so as to control the air intake or exhaust of the air chamber (22), until the actual pressure value of the air chamber (22) is equal to the preset pressure value. In the automatic control process of the air chamber pressure, the first wave spring assembly (4) and the fourth wave spring assembly (7) play a proportional control role, and the second wave spring assembly (5) and the third wave spring assembly (6) play an integral control role.

2. The automatic proportional-integral pressure controller according to claim 1, characterized in that: The second wave spring assembly (5) and the third wave spring assembly (6) are arranged on the inner side, and the first wave spring assembly (4) and the fourth wave spring assembly (7) are arranged on the outer side, so as to enhance the proportional control effect and weaken the integral control effect; Alternatively, the second wave spring assembly (5) and the third wave spring assembly (6) are arranged on the outside, and the first wave spring assembly (4) and the fourth wave spring assembly (7) are arranged on the inside, so as to enhance the integral control effect and weaken the proportional control effect.

3. The automatic proportional-integral pressure controller according to claim 1, characterized in that: The fixed plate (1) and the floating plate (2) are provided with transverse moving grooves and limiting grooves, and protrusions are provided at both ends of each wave spring assembly. The protrusions at both ends of each wave spring assembly are respectively slidably matched with the moving grooves on the fixed plate (1) and the floating plate (2), and the two ends of each wave spring assembly are fixed in the limiting grooves of the fixed plate (1) and the floating plate (2) by screws. When the size or stiffness of the four wave spring assemblies deviates due to manufacturing errors, thereby causing the floating plate (2) to be subjected to unbalanced force, the floating plate (2) is adjusted to a force-balanced state by loosening the fixing screws at both ends and fine-tuning the fixed position of the wave spring assembly.

4. The automatic proportional-integral pressure controller according to claim 1, wherein: The nozzle (10) is mounted on the fixed plate (1) via a second connecting block (11); a vertical limiting groove is provided on the second connecting block (11); a screw passes through the vertical limiting groove to fix the second connecting block (11) on the fixed plate (1); and the initial distance between the nozzle (10) and the baffle (9) can be roughly adjusted by adjusting the position of the screw in the limiting groove.

5. The automatic proportional-integral pressure controller according to claim 1, wherein: The installation position of the first connecting block (8) on the floating plate (2) can be adjusted left and right.

6. The automatic proportional-integral pressure controller according to claim 1, wherein: Two threaded holes are provided on the first connecting block (8), one end of the baffle (9) is fixedly mounted on the first connecting block (8) by a screw in cooperation with one of the threaded holes, and another screw passes through the other threaded hole from below and presses upward against the lower surface of the baffle (9), and the initial distance between the baffle (9) and the nozzle (10) can be fine-tuned by adjusting the protruding length of the other screw.

7. The automatic proportional-integral pressure controller according to claim 1, wherein: The elastic mechanism (3) comprises an upper support seat (31), an upper support piece (32), a horizontal elastic piece (33), a vertical elastic piece (34), a lower support piece (35) and a lower support seat (36); the upper support seat (31) is connected to the floating plate (2); the lower support seat (36) is connected to the fixed plate (1); the upper support piece (32) is mounted on the upper support seat (31); the lower support piece (35) is mounted on the lower support seat (36); the horizontal elastic piece (33) and the vertical elastic piece (34) are respectively connected to the upper support piece (32) and the lower support piece (35); when the floating plate (2) rotates, the horizontal elastic piece (33) and the vertical elastic piece (34) are elastically deformed and generate a torque in a reverse direction, so that the floating plate (2) returns to its original shape when no force is applied.

8. The automatic proportional-integral pressure controller according to claim 7, characterized in that: The restoring torque of the elastic mechanism (3) is adjusted by adjusting the thickness of the horizontal elastic piece (33) and the vertical elastic piece (34).

9. The automatic proportional-integral pressure controller according to claim 1, wherein: A throttle valve (14) is also provided between the air storage chamber (15) and the output chamber (122) of the pneumatic amplifier (12).

10. The automatic proportional-integral pressure controller according to claim 1, wherein: The wave spring assembly comprises an upper cover plate (41), a wave spring (42) and a lower cover plate (43). The upper end of the upper cover plate (41) is connected to the floating plate (2), and the lower end of the lower cover plate (43) is connected to the fixed plate (1). The two ends of the wave spring (42) are respectively connected to the upper cover plate (41) and the lower cover plate (43). The lower cover plate (43) is provided with an air inlet (431) for communicating with an external air source. The air inlet (431) is connected to the air inlet of the wave spring (42). When the air pressure input by the external air source enters the wave spring (42), the wave spring (42) extends upward to push the floating plate (2) to rotate.

Images