Intermittent constant pressure valve and use thereof

Abstract

The application belongs to the technical field of pneumatic actuators, and discloses an intermittent constant pressure valve, which comprises a valve body, a valve base and a valve rod, the valve rod is located in the valve body, the valve base is located at one end of the valve body, the valve base is coaxially provided with a central hole penetrating through the axial two ends, the valve rod is connected with a valve core at one end close to the valve base, the valve rod is coaxially provided with an axial hole penetrating through the axial two ends, the valve rod is provided with an air inlet hole on one side in communication with the axial hole, one end of the valve rod is located in the valve body, the other end of the valve rod extends out of the valve body, a guide sleeve is coaxially arranged on the outer periphery of the valve rod, a disc spring set is arranged on the outer periphery of the guide sleeve, the disc spring set is located on the outer side of the valve body, a pressure regulating part is arranged on the outer side of the guide sleeve, the pressure regulating part is connected with the valve body, a pre-tightening part is connected with the valve rod at the end extending out of the valve body, the disc spring set is located between the pressure regulating part and the pre-tightening part. The application can improve the service life of the disc spring, reduce the number of disc springs used, and thus reduce the volume of the whole constant pressure valve.

Description

Technical Field

[0001] This invention relates to the field of pneumatic actuator technology, specifically to a constant pressure valve with intermittent action and its application. Background Technology

[0002] In industrial production and applications, a stable air pressure is often required as the driving force for intermittent motion, such as in pneumatic actuators, pneumatic tools, and pneumatic rifles. Traditional intermittent pressure-regulating valves (hereinafter referred to as conventional valves) use a disc spring assembly with an end-mounted pressure adjusting screw for pressure regulation and locking to achieve constant pressure. However, due to the constant gap between the disc spring assembly and the valve stem, the disc spring can misalign axially during operation, resulting in a component of force on the disc spring that is not parallel to the axial direction. Subsequently, under the alternating shearing action of this component force, the disc spring quickly fatigues and fails, leading to unstable constant pressure. Furthermore, the randomness of the disc spring misalignment causes instability in constant pressure after each operation.

[0003] Furthermore, in traditional valves, the disc springs are typically housed within the valve body for limiting movement, thus restricting their outer diameter. Consequently, for valves with the same outer diameter, reducing the size of the disc spring by one size and increasing the number of disc springs for the same pressure regulation results in an increase in the length and volume of the valve body. Summary of the Invention

[0004] This invention provides an intermittently operating constant pressure valve, which aims to improve the lifespan of disc springs and reduce the number of disc springs used, thereby reducing the overall size of the constant pressure valve.

[0005] This invention provides an intermittently operating constant pressure valve, comprising a valve body, a valve base, and a valve stem. The valve stem is located within the valve body, and the valve base is located at one end of the valve body. The valve base has a central hole coaxially extending through both ends of its axial direction. A valve core is connected to one end of the valve stem near the valve base. The valve stem also has an axial hole coaxially extending through both ends of its axial direction. An air inlet is provided on one side of the valve stem, communicating with its axial hole. One end of the valve stem is located within the valve body, and the other end extends out of the valve body. A guide sleeve is coaxially fitted around the outer periphery of the valve stem. A disc spring assembly is fitted around the outer periphery of the guide sleeve, located outside the valve body. A pressure regulating component is fitted around the outer side of the guide sleeve and connected to the valve body. A preload component for axially adjusting the pressure of the disc spring assembly is connected to one end of the valve stem extending out of the valve body. The disc spring assembly is located between the pressure regulating component and the preload component.

[0006] Compared with the prior art, the present invention has the following advantages and beneficial effects:

[0007] The constant pressure valve in this invention is installed inside a pipeline, dividing the pipeline into a constant pressure chamber on the left and a high pressure chamber on the right. Initially, high-pressure gas flows from the high pressure chamber into the valve body cavity through the central hole of the valve base, then through the gap between the valve base and the valve core, through the gap between the valve stem and the valve body, then into the radial air inlet of the valve stem, then into the axial hole of the valve stem, and finally into the constant pressure chamber. As the pressure in the constant pressure chamber gradually increases, the force on the valve stem side of the constant pressure chamber is greater than the force on the high pressure chamber side, causing the valve stem to move towards the valve base until the valve core and valve seat achieve a seal.

[0008] When the gas in the constant pressure chamber is consumed, the valve stem loses its balance. The resultant force acting on the valve stem from the high-pressure chamber end to the left is greater than the resultant force acting on the valve stem from the constant pressure chamber end to the right. At this point, the valve stem moves to the left, the valve core and valve base separate, and the valve is open, allowing high-pressure gas to re-enter the constant pressure chamber. When the pressure in the constant pressure chamber reaches a certain level, causing the resultant force on the left side of the valve stem to be greater than the resultant force on the right side, the valve stem moves to the right, thus sealing the central hole of the valve core and valve base again, thereby completing the valve opening and closing cycle.

[0009] In existing technologies, disc spring assemblies are typically located inside the valve body, not exposed on the outside. However, in pneumatic actuator applications, the constant pressure chamber is often a space with a limited diameter. Based on the characteristics of disc spring elasticity coefficients, a larger diameter and thicker wall result in a higher elasticity coefficient. The more disc springs overlap in the same direction, the more prone they are to adhesion and axial misalignment, leading to inconsistencies between rebound force and backpressure time. Arranging disc springs of the largest diameter within the limited constant pressure space helps reduce the number of disc springs, decrease the overall length of the constant pressure valve, and effectively expand the constant pressure chamber space. Simultaneously, it effectively increases the disc spring elasticity coefficient, making the disc springs more durable when subjected to the same amount of alternating stress.

[0010] In this design, the disc spring assembly is located on the outside of the valve body. This avoids the limitation on disc spring size, such as in existing technologies where the disc spring is built into the constant pressure valve, which restricts the size of the disc spring and reduces its elasticity. The outer location of the disc spring assembly in this design maximizes the disc spring diameter. With the same valve outer diameter, there is no need to reduce the size of the disc spring assembly or increase the number of disc springs, thus reducing the number of disc springs and increasing their lifespan. Furthermore, it does not increase the overall length of the constant pressure valve, thereby avoiding an increase in its overall volume and achieving a balance between a small space and a large constant pressure valve size.

[0011] Furthermore, in the existing technology, the disc spring assembly is located inside the valve body, which is inconvenient to operate when adjustment is required. In contrast, the disc spring assembly in this solution is located outside the valve body, making adjustment much more convenient.

[0012] In this invention, a guide sleeve is provided on the outer periphery of the valve stem. In actual design, the outer diameter of the guide sleeve and the inner diameter of the disc spring have a small tolerance. The guide sleeve and the disc spring assembly cooperate to form a whole. The guide sleeve slides simultaneously with the deformation of the disc spring. That is, either the guide sleeve and the disc spring move together and are compressed or extended, or neither the guide sleeve nor the disc spring moves.

[0013] Furthermore, the guide sleeve and disc spring assembly serve as axial limiters. The guide sleeve prevents radial misalignment of the disc springs, thus avoiding axial misalignment and preventing the disc springs from experiencing non-parallel force separation that could lead to fatigue failure. This ensures uniform stress distribution on the guide sleeve and disc spring assembly, preventing isolated damage or fatigue of a single disc spring due to localized stress, which could then affect the entire assembly. This addresses the issues of short disc spring life and unstable constant pressure. The addition of the guide sleeve also allows the entire disc spring assembly to move simultaneously, improving the stress distribution on the disc springs and enabling them to achieve back pressure in a very short time.

[0014] This invention also includes a pressure regulating component and a pre-tightening component, which can pre-tighten and regulate the pressure of the disc spring assembly. Thus, under the same constant pressure chamber force, the disc spring assembly can utilize the elastic force within different deformation ranges of the disc spring. Theoretically, this can more effectively improve the lifespan of the disc spring in the constant pressure valve and optimize the back pressure time. In this invention, the pressure regulating component mainly adjusts the movement space of the valve stem. This movement space is related to the compression distance of the disc spring assembly. The further the valve stem is adjusted away from the valve base, the greater the required compression of the disc spring assembly. This is because it results in a greater distance between the valve core at the end of the valve stem and the valve base, a greater stroke, and a greater required compression of the disc spring assembly. Consequently, a greater required disc spring reaction force is needed to push the valve core at the end of the valve stem towards the valve base to abut against the central hole for sealing.

[0015] In practice, the distance between the valve core and the valve base is relatively short. At this time, the disc spring does not need to be compressed too much to achieve the purpose of the valve core blocking the center hole. The pressure in the constant pressure chamber is also relatively small to achieve a seal between the valve core and the center hole. Therefore, pre-adjustment is not required at this time, but there may be situations where the pressure requirements are not met.

[0016] To ensure the constant pressure chamber meets the pressure requirements, the preload mechanism needs to be tightened to partially compress the disc spring assembly. This compression creates a pre-elastic force, requiring sufficient pressure within the constant pressure chamber to further compress the disc spring assembly and push the valve stem to the right, sealing the center hole with the valve core. This ensures the pressure within the constant pressure chamber meets the usage requirements. In practical applications, the operating range of the disc spring assembly can be selected based on the actual pressure requirements, allowing for the adjustment of either the preload mechanism or the pressure regulating mechanism. This invention is applicable to disc spring assemblies of varying numbers and arrangements.

[0017] Furthermore, the pre-tightening component is a pre-tightening nut, which is threadedly connected to the valve stem; the pressure adjusting component is a pressure adjusting nut, which is threadedly connected to the inner wall of the valve body; and the guide sleeve is coaxially slidingly fitted with the adjusting nut.

[0018] Beneficial effects: The preload nut in this solution can preload the disc spring, and by rotating the pressure adjusting nut, the position of the pressure adjusting nut can be changed, thereby adjusting the preload pressure on the disc spring according to the actual situation.

[0019] Furthermore, the disc spring assembly includes multiple pairs of disc springs, with the concave surfaces of each pair of disc springs facing each other, and a flat washer provided between each pair of disc springs.

[0020] Beneficial effects: In this invention, a flat washer is provided between each pair of disc springs facing each other, which makes the force on the disc springs more uniform, thereby avoiding failure due to shear force. According to relevant research, this setting can increase the service life of the disc springs by up to 6 times. This is the first application of this technology in intermittent constant pressure valves, both domestically and internationally.

[0021] Furthermore, the thickness of the flat pad is greater than the thickness of the disc spring, and the outer diameter of the flat pad is greater than or equal to the maximum outer diameter of the multiple disc springs after compression.

[0022] Beneficial effects: This setup can improve the uniformity of force on each set of disc springs, and the force is more stable, making it less prone to failure.

[0023] Furthermore, the guide sleeve can slide simultaneously with the deformation of the disc spring assembly, and the sliding distance of the guide sleeve is the total deformation of the disc spring assembly.

[0024] Beneficial effects: The guide sleeve enables the disc spring assembly to move simultaneously, effectively improving the stress on the disc springs and preventing misalignment when the disc spring assembly moves axially, thus effectively increasing the lifespan of the disc springs.

[0025] Furthermore, a limiting part is coaxially provided on the valve stem, the diameter of the limiting part being larger than the diameter of the valve stem. A stepped hole matching the shape formed by the valve stem and the limiting part is opened in the valve body. The stepped hole includes a large hole and a small hole that are interconnected. The limiting part is located in the large hole of the stepped hole, and the distance between the limiting part and the end of the large hole near the small hole is greater than the distance between the valve core and the valve base.

[0026] Beneficial effects: The stepped hole in this design can limit the limiting part on the valve stem, thereby limiting the maximum sliding distance of the valve stem and ensuring the stable operation of the entire constant pressure valve. In addition, the distance between the limiting part and the end of the large hole near the small hole is greater than the distance between the valve core and the valve base, which can ensure that the valve core abuts against the center hole and seals the center hole.

[0027] Furthermore, sealing rings are provided between the valve base and the valve body, between the valve stem and the valve body, and between the limiting part and the valve body.

[0028] Beneficial effects: The sealing ring prevents gas leakage and allows gas to smoothly enter the valve stem, thus enabling gas to move from the high-pressure chamber to the constant-pressure chamber, which can then be used as a driving force to drive the movement of other components.

[0029] Furthermore, the valve base is threadedly connected to the valve body.

[0030] Beneficial effects: In this solution, the valve base not only achieves sealing with the valve body through the sealing ring, but also achieves a dual sealing effect of thread sealing and sealing ring sealing through the threaded connection between the two, which can effectively improve the sealing performance of the device.

[0031] Furthermore, an indicator hole communicating with the stepped hole is provided on one side of the valve body, and the indicator hole is a through hole structure.

[0032] Beneficial effects: The indicator hole in this solution can be used as a basis for judging whether there is gas leakage. The sealing performance of the constant pressure valve can be judged by whether there is gas leakage through the indicator hole, so as to facilitate timely replacement of the sealing ring or corresponding sealing.

[0033] An application of an intermittently acting constant pressure valve, wherein the aforementioned intermittently acting constant pressure valve is installed in a pipeline and divides the pipeline into a high-pressure chamber and a constant-pressure chamber, wherein the high-pressure chamber contains high-pressure gas, and the high-pressure gas in the high-pressure chamber flows into the valve body cavity from the central hole of the valve base, and a sealing ring is provided between the valve body and the pipeline.

[0034] Beneficial effects: The constant pressure valve in this solution is applied inside the pipeline to form a high-pressure chamber and a constant pressure chamber, which is used to regulate the gas pressure and make the gas pressure reach a balance and stability, so as to provide a stable gas source for driving other devices. Attached Figure Description

[0035] The accompanying drawings, which are included to provide a further understanding of embodiments of the invention and form part of this application, do not constitute a limitation thereof. In the drawings:

[0036] Figure 1 This is a longitudinal cross-sectional view of an embodiment of an intermittently operating constant pressure valve according to the present invention;

[0037] Figure 2 This is a schematic diagram of the installation of an intermittently acting constant pressure valve in a pipeline according to the present invention;

[0038] Figure 3 This is an exploded view of an embodiment of an intermittently operating constant pressure valve according to the present invention.

[0039] The attached diagram shows the following components and their corresponding names: Valve body 1, Valve base 2, Sealing ring I 3, Valve core 4, Sealing ring II 5, Valve stem 6, Sealing ring III 7, Sealing ring IV 8, Guide sleeve 9, Sealing ring V 10, Pressure adjusting nut 11, Disc spring 12, Flat washer 13, Preload nut 14, Pipe 15, Air inlet 16, Axial hole 17, Center hole 18, Limiting part 19, Indicator hole 20. Detailed Implementation

[0040] To make the objectives, technical solutions, and advantages of the present invention clearer, the present invention will be further described in detail below with reference to the embodiments and accompanying drawings. The illustrative embodiments and descriptions of the present invention are only used to explain the present invention and are not intended to limit the present invention.

[0041] like Figures 1-3 As shown, this embodiment provides an intermittently acting constant pressure valve, including a valve body 1, a valve base 2, and a valve stem 6. The valve stem 6 is located inside the valve body 1, and the valve base 2 is located at the left end inside the valve body 1 and extends into the valve body 1 for threaded connection. A sealing ring I3 is provided between the valve base 2 and the valve body 1, thus achieving a dual sealing effect between the valve base 2 and the valve body 1 through both threaded sealing and sealing ring sealing. In actual design, two sealing rings can also be used directly between the valve base 2 and the valve body 1 to achieve a dual sealing effect.

[0042] Both the valve body 1 and the valve stem 6 have hollow interiors. The valve base 2 has a central hole 18 that runs through both ends of its axial direction. The diameter of the central hole 18 is relatively small. In this embodiment, the diameter of the central hole 18 is 5mm, which improves its sealing performance later.

[0043] A valve core 4 is connected to one end of the valve stem 6 near the valve base 2. The valve core 4 has a T-shaped structure and is inserted into the right end of the valve stem 6 with an interference fit. In this embodiment, the valve core 4 is made of PEEK material, which has a high density and is more durable. There is a gap between the right side of the valve stem 6 and the inner wall of the valve body 1. The valve stem 6 has an axial hole 17 that passes through both ends of its axial direction. An air inlet hole 16 communicating with the axial hole 17 is opened on one side of the valve stem 6. The air inlet hole 16 is located close to the valve core 4 and is arranged along the axial direction perpendicular to the valve stem 6.

[0044] The right end of the valve stem 6 is located inside the valve body 1, and the left end of the valve stem 6 extends out of the valve body 1. A guide sleeve 9 is coaxially sleeved on the outer periphery of the valve stem 6. A pre-tightening component for axially adjusting the pressure of the disc spring assembly is connected to the end of the valve stem 6 extending out of the valve body 1. A disc spring assembly is sleeved on the outer periphery of the guide sleeve 9. Both the disc spring assembly and the pre-tightening component are located on the outside of the valve body 1. A pressure adjusting component is sleeved on the outside of the guide sleeve 9. The pressure adjusting component is connected to the left end of the valve body. The disc spring assembly is located between the pressure adjusting component and the pre-tightening component. Specifically, in this embodiment, the pre-tightening component is a pre-tightening nut 14. In this embodiment, the pre-tightening nut 14 is threadedly connected to the end of the valve stem 6 extending out of the valve body 1. The pressure adjusting component is a pressure adjusting nut 11. The pressure adjusting nut 11 is threadedly connected to the inner wall of the valve body 1.

[0045] Combination Figure 1 and Figure 3 As shown, the pressure adjusting nut 11 is T-shaped and is coaxially and slidingly fitted with the guide sleeve 9, allowing the guide sleeve 9 to move freely axially within the pressure adjusting nut 11. The disc spring assembly includes multiple pairs of disc springs 12, with the concave surfaces of each pair facing each other. In this embodiment, five pairs of disc springs 12 are provided. Between each pair of disc springs 12 is a flat washer 13 made of the same material and with a thickness greater than that of the disc spring 12. The outer diameter of the flat washer 13 is greater than or equal to the maximum outer diameter of the multiple pairs of disc springs 12 after compression, and it maintains a clearance fit with the inner diameter of the installation pipe 15. The inner diameter of the flat washer 13 and the outer diameter of the guide sleeve 9 maintain a small tolerance clearance fit.

[0046] like Figure 1 As shown, in this embodiment, the tolerance between the outer diameter of the guide sleeve 9 and the inner diameter of the disc spring 12 is small, but it still satisfies the requirement that after the disc spring assembly is compressed, the disc spring 12 and the guide sleeve 9 are still in a clearance fit. The guide sleeve 9 can slide simultaneously with the deformation of the disc spring assembly, and the sliding distance of the guide sleeve 9 is the total deformation of the disc spring assembly.

[0047] In this embodiment, a limiting part 19 is coaxially provided on the valve stem 6. The limiting part 19 is located on the right side of the valve stem 6, and its diameter is larger than that of the valve stem 6. The limiting part 19 is integrally formed with the valve stem 6. The limiting part 19 is formed when the valve stem 6 is machined on a lathe, making the valve stem 6 as a stepped shaft shape. A stepped hole matching the shape formed by the valve stem 6 and the limiting part 19 is opened in the valve body 1. The stepped hole includes a large hole and a small hole that are interconnected. Here, the hole with the larger inner diameter in the stepped hole is the large hole, and the hole with the smaller inner diameter is the small hole. The limiting part 19 is located in the large hole of the stepped hole, and the distance between the limiting part 19 and the end of the large hole near the small hole is greater than the distance between the valve core 4 and the valve base 2. This ensures that the valve core 4 can block the central hole 18 to achieve a seal. A sealing ring III7 is provided between the valve stem 6 and the valve body 1, and the sealing ring III7 is located inside the small hole of the stepped hole. A sealing ring IV8 is provided between the limiting part 19 and the valve body 1.

[0048] A pointer hole 20 communicating with the stepped hole is provided on one side of the valve body 1. The pointer hole 20 is a through hole structure and is located between the sealing ring III7 and the sealing ring IV8.

[0049] like Figure 2 As shown, this embodiment also discloses the application of an intermittently acting constant pressure valve. The aforementioned intermittently acting constant pressure valve is installed and confined within the pipeline 15, thereby dividing the pipeline 15 into a high-pressure chamber and a constant-pressure chamber. The high-pressure chamber contains high-pressure gas, which flows into the inner cavity of the valve body 1 through the central hole 18 of the valve base 2. A sealing ring is provided between the valve body 1 and the pipeline 15. In this embodiment, sealing ring V10 and sealing ring II5 are respectively provided on the left and right sides of the valve body 1. Sealing rings V10 and II5 seal the valve body 1 and the pipeline 15, thereby preventing gas from the high-pressure chamber from flowing through the gap between the pipeline 15 and the valve body 1 and affecting the stability of the gas source pressure in the constant-pressure chamber.

[0050] The specific implementation process is as follows: Figure 3 As shown, based on the elastic properties, materials, and different mechanical properties of the disc spring 12 produced by the manufacturer, the adjustment nut 11 or the preload nut 14 is selected to determine which range of the disc spring 12's elastic force needs to be utilized, whether it is the elastic force generated at the beginning of the disc spring 12 or the elastic force generated after preload and secondary compression.

[0051] In this embodiment, the pressure adjusting nut 11 is tightened to the right, so that the right end of the pressure adjusting nut 11 abuts against the left end of the limiting part 19, and the left part of the pressure adjusting nut 11 abuts against the left end of the valve body 1. The adjustment of the pressure adjusting nut 11 achieves the initial compression of the disc spring 12 assembly. However, the compression force generated by the disc spring assembly at this time is small and may not meet the pressure requirements of the constant pressure chamber. Therefore, in order to make the constant pressure chamber meet the pressure requirements, the preload nut 14 is tightened, and the valve stem 6 will move to the right. At the same time, the disc spring assembly is compressed to generate a preload force. At this time, the constant pressure chamber needs to have a sufficiently large pressure to allow the disc spring assembly to be further compressed a second time and push the valve stem 6 to move to the right to achieve the seal between the valve core 4 and the center hole 18 of the valve base 2.

[0052] In this embodiment, the preload nut 14 initially compresses the disc spring assembly, causing it to generate a certain preload or rebound force. Once the constant pressure chamber has pressure, the disc spring assembly will continue to compress to the right, thus sealing the valve core 4 and the center hole 18. This embodiment adjusts the preload nut 14, which increases the constant pressure of the disc spring 12. When the preload nut 14 is tightened, the disc spring 12 assembly itself has a preload and rebound force. Therefore, the constant pressure chamber needs to have a large pressure to continue compressing the disc spring 12 assembly, so that the valve core 4 and the center hole 18 can be successfully sealed together. This embodiment can meet the requirement that the constant pressure chamber has a sufficiently large pressure.

[0053] Initially, high-pressure gas comes from the high-pressure chamber on the right side and flows into the inner cavity of the valve body 1 through the central hole 18 of the valve base 2. Then, it passes through the gap between the valve base 2 and the valve core 4, and through the gap between the valve stem 6 and the valve body 1, and enters the radially arranged air inlet 16 of the valve stem 6, and then enters the axial hole 17 of the valve stem 6, and then enters the constant pressure chamber from the axial hole 17 of the valve stem 6.

[0054] As the pressure in the constant pressure chamber gradually increases, a difference exists between the left and right cross-sections of the valve stem 6. Therefore, when the force on the constant pressure chamber side of the valve stem 6 is greater than the force on the high pressure chamber side, the valve stem 6 will move to the right until the valve core 4 and the valve base 2 abut against each other, blocking the central hole 18 of the valve seat and achieving a seal. At this point, neglecting friction, the valve stem 6 achieves equilibrium under the air pressure of the two chambers, the elastic force of the disc spring 12, and the sealing reaction force.

[0055] like Figure 2 As shown, after the gas in the constant pressure chamber is consumed over a period of time, the valve stem 6 loses its force balance. The resultant force acting on the valve stem 6 from the high-pressure chamber gas end to the left is greater than the resultant force acting on the valve stem 6 from the constant pressure chamber end to the right. At this time, the valve stem 6 moves to the left. The valve core 4 and the valve seat separate, and the valve is in the open state. At this time, the high-pressure gas passes through the valve body 1 cavity, enters the radially arranged air inlet 16 of the valve stem 6, then enters the axial hole 17 of the valve stem 6, and then enters the constant pressure chamber. When the pressure in the constant pressure chamber reaches a certain level, the resultant force on the left side of the valve stem 6 becomes greater than the resultant force on the right side, and the valve stem 6 moves to the right, thereby sealing the valve core 4 and the valve seat, realizing the opening and closing cycle.

[0056] When sealing rings II5 and V10 are damaged, the constant pressure valve will leak externally. In this case, indicator hole 20 can be used as a leakage indicator. If sealing ring II5 is damaged and causes leakage, the pressure gauge reading in the constant pressure chamber will remain unchanged even when no air is being used. At this time, air inlet 16 will continue to leak until the air supply to the high-pressure chamber is exhausted.

[0057] If sealing ring V10 is damaged, causing leakage, the pressure in the constant pressure chamber will fluctuate continuously, and the high pressure chamber will continuously replenish the air pressure until the air supply in the high pressure chamber is exhausted. When sealing rings III7 and IV8 are damaged, the constant pressure valve will experience internal leakage: when sealing ring III7 is damaged, the indicator hole 20 will leak air every time the valve is opened; when sealing ring IV8 is damaged, the pressure in the constant pressure chamber will fluctuate frequently, the indicator hole 20 will leak continuously, and the valve core 4 will continuously open and close until the air supply in the high pressure chamber is exhausted.

[0058] The specific embodiments described above further illustrate the purpose, technical solution, and beneficial effects of the present invention. It should be understood that the above description is only a specific embodiment of the present invention and is not intended to limit the scope of protection of the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A constant pressure valve with intermittent action, comprising a valve body, a valve base, and a valve stem, wherein the valve stem is located within the valve body, the valve base is located at one end of the valve body, the valve base has a central hole coaxially extending through both ends of the central hole, a valve core is connected to one end of the valve stem near the valve base, the valve stem has an axial hole coaxially extending through both ends of the axial hole, and an air inlet is provided on one side of the valve stem communicating with the axial hole, characterized in that, One end of the valve stem is located within the valve body, and the other end extends out of the valve body. A guide sleeve is coaxially fitted around the outer periphery of the valve stem. A disc spring assembly is fitted around the outer periphery of the guide sleeve, located outside the valve body. A pressure regulating component is fitted around the outer side of the guide sleeve and connected to the valve body. A preload component for axially adjusting the pressure of the disc spring assembly is connected to the end of the valve stem extending out of the valve body. The disc spring assembly is located between the pressure regulating component and the preload component. The preload component is a preload nut, which is threadedly connected to the valve stem. The component is a pressure adjusting nut, which is threaded to the inner wall of the valve body. The guide sleeve is coaxially slidingly fitted with the pressure adjusting nut. A limiting part is coaxially provided on the valve stem. The diameter of the limiting part is larger than the diameter of the valve stem. A stepped hole matching the shape formed by the valve stem and the limiting part is opened in the valve body. The stepped hole includes a large hole and a small hole that are interconnected. The limiting part is located in the large hole of the stepped hole, and the distance between the limiting part and the end of the large hole near the small hole is greater than the distance between the valve core and the valve base.

2. The intermittently acting constant pressure valve according to claim 1, characterized in that, The disc spring assembly includes multiple pairs of disc springs, with the concave surfaces of each pair of disc springs facing each other, and a flat washer provided between each pair of disc springs.

3. The intermittently acting constant pressure valve according to claim 2, characterized in that, The thickness of the flat pad is greater than the thickness of the disc spring, and the outer diameter of the flat pad is greater than or equal to the maximum outer diameter of the multiple disc springs after compression.

4. The intermittently acting constant pressure valve according to claim 1, characterized in that, The guide sleeve can slide simultaneously with the deformation of the disc spring assembly, and the sliding distance of the guide sleeve is the total deformation of the disc spring assembly.

5. The intermittently acting constant pressure valve according to claim 1, characterized in that, Sealing rings are provided between the valve base and the valve body, between the valve stem and the valve body, and between the limiting part and the valve body.

6. The intermittently acting constant pressure valve according to claim 5, characterized in that, The valve base is threadedly connected to the valve body.

7. The intermittently acting constant pressure valve according to claim 1, characterized in that, The valve body has an indicator hole on one side that communicates with the stepped hole, and the indicator hole is a through hole structure.

8. A method for applying an intermittently acting constant pressure valve, characterized in that, An intermittently acting constant pressure valve according to any one of claims 1-7 is installed in a pipeline and the pipeline is divided into a high-pressure chamber and a constant pressure chamber. The high-pressure chamber contains high-pressure gas, which flows into the valve body cavity from the central hole of the valve base. A sealing ring is provided between the valve body and the pipeline.

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