A metal-sealed breather valve with controlled reseating impact energy and its design method

Abstract

This invention relates to the field of breather valve technology, specifically a metal-sealed breather valve with controlled reseating impact energy and its design method. The valve includes a valve body, a valve seat, and a valve disc assembly movable relative to the valve seat between a closed position and a maximum open position. A sealing mating surface is formed between the valve disc assembly and the valve seat, comprising a first smooth surface and a second smooth surface. By providing a sealing mating surface composed of the first and second smooth surfaces between the valve disc assembly and the valve seat, this invention improves the fitting accuracy of the valve disc assembly after reseating, thereby reducing leakage and improving sealing stability. Simultaneously, by coordinating the mass, maximum opening height, and second pressure diameter of the valve disc assembly, the single reseating impact energy when the valve disc assembly falls from the maximum open position to the closed position does not exceed an upper limit of impact energy determined based on the allowable damage level of the first and second smooth surfaces.

Description

Technical Field

[0001] This invention relates to the field of breather valve technology, and in particular to a metal-sealed breather valve with controlled reseating impact energy and its design method. Background Technology

[0002] Breather valves are safety accessories widely used in storage tanks, pressure vessels, and related process equipment. Existing breather valves typically consist of a valve body, a valve seat, and a valve disc assembly that can move up and down relative to the valve seat. The valve disc assembly opens under tank pressure and closes by returning to the valve seat after the pressure recedes. To reduce leakage, existing technologies often improve sealing performance by using sealing rings or gaskets between the valve disc and valve seat, or by increasing the machining precision of the contact surfaces. Some designs also employ mating smooth sealing surfaces to improve the fit after reseating and reduce micro-leakage. However, in actual operation, to meet flow capacity requirements, the breather valve often needs a certain opening height for the valve disc assembly. When the valve disc assembly returns from its maximum open position to the closed position after depressurization or refilling, it causes a reseating impact on the valve seat. Especially in structures using smooth sealing surfaces, although the smooth surface improves sealing, it is more sensitive to localized pressure marks, scratches, and damage to the mating surfaces caused by repeated impacts.

[0003] Current breather valve designs typically focus on performance indicators such as set pressure, flow rate, and sealing leakage, while neglecting the impact energy during the valve disc assembly's reseating process. If the maximum opening height of the valve disc assembly is simply increased to improve flow rate, the impact during reseating often increases. Furthermore, if there is a lack of proper matching between the valve disc assembly's mass, the pressure-bearing area, and the opening height, long-term opening and closing can easily lead to accumulated damage to the sealing surfaces, causing wear, indentations, or reseating misalignment on smooth sealing surfaces. This results in decreased sealing performance, increased leakage, and shortened service life. These problems are particularly pronounced in applications requiring low leakage.

[0004] Therefore, the existing technology still lacks a breather valve structure and corresponding design method that can simultaneously meet the requirements of low leakage sealing and reseating safety. In particular, there is a lack of a low leakage and high safety breather valve that controls the reseating impact of the valve disc assembly to reduce damage to the smooth sealing surface and improve overall safety. Summary of the Invention

[0005] In this section, as well as in the abstract and title of this application, some simplifications or omissions may be made to avoid obscuring the purpose of this section, the abstract, and the title of this application, and such simplifications or omissions shall not be used to limit the scope of the invention.

[0006] To address the shortcomings of existing technologies, one objective of this invention is to provide a metal-sealed breather valve with controlled reseating impact energy.

[0007] To achieve the above objectives, the present invention adopts the following technical solution: a metal-sealed breather valve with controlled reseating impact energy, comprising a valve body, a valve seat, and a valve disc assembly movable relative to the valve seat between a closed position and a maximum open position. A sealing mating surface is formed between the valve disc assembly and the valve seat, the sealing mating surface including a first smooth surface M1 and a second smooth surface M2. In the closed position, the valve disc assembly corresponds to a first pressure-bearing region S1, the equivalent diameter of which is a first pressure-bearing diameter d1. In the maximum open position, the valve disc assembly corresponds to a second pressure-bearing region S2, the equivalent diameter of which is a second pressure-bearing diameter d2, and the second pressure-bearing diameter d2 is greater than the first pressure-bearing diameter d1. The mass m, maximum opening height H, and second pressure-bearing diameter d2 of the valve disc assembly are coordinated to ensure that the single reseating impact energy E when the valve disc assembly falls from the maximum open position back to the closed position does not exceed an upper limit of impact energy E0. The upper limit of impact energy E0 is an upper limit of single reseating impact energy determined based on the allowable damage level of the first smooth surface M1 and the second smooth surface M2.

[0008] As a preferred embodiment of the metal-sealed breather valve with controlled reseating impact energy according to the present invention, wherein the single reseating impact energy E satisfies the following formula: , Where g is the acceleration due to gravity.

[0009] As a preferred embodiment of the metal-sealed breather valve with controlled reseating impact energy according to the present invention, wherein: under the condition that the first pressure-bearing diameter d1, the second pressure-bearing diameter d2, and the upper limit of impact energy E0 are determined, the mass m of the valve disc assembly and the maximum opening height H satisfy: .

[0010] As a preferred embodiment of the metal-sealed breather valve with controlled reseating impact energy according to the present invention, wherein: the second pressure-bearing diameter d2 satisfies: .

[0011] As a preferred embodiment of the metal-sealed breather valve with controlled reseating impact energy according to the present invention, wherein: the first smooth surface M1 and the second smooth surface M2 are both metal sealing surfaces; wherein, the upper limit of impact energy E0 is the upper limit of single reseating impact energy allowed to maintain the predetermined sealing performance of the first smooth surface M1 and the second smooth surface M2 within a predetermined number of opening and closing cycles.

[0012] As a preferred embodiment of the metal-sealed breather valve with controlled reseating impact energy according to the present invention, the surface roughness Ra of the first smooth surface M1 and the second smooth surface M2 is not greater than 0.1 μm.

[0013] As a preferred embodiment of the metal-sealed breather valve with controlled reseating impact energy according to the present invention, the valve disc assembly includes a guide portion, which is used to limit the sway of the valve disc assembly during the process of falling back from the maximum open position to the closed position, so as to make the first smooth surface M1 and the second smooth surface M2 reseating and aligning.

[0014] As a preferred embodiment of the metal-sealed breather valve with controlled reseating impact energy according to the present invention, the valve disc assembly includes a pressure-bearing part and a weight-reducing part, the second smooth surface M2 is formed on the pressure-bearing part, and the weight-reducing part is provided to avoid the area overlapping with the second smooth surface.

[0015] To address the shortcomings of existing technologies, another objective of this invention is to provide a design method for a metal-sealed breather valve.

[0016] The present invention adopts the following technical solution: a design method for a metal-sealed breather valve, comprising: determining an upper limit of impact energy E0 based on the allowable damage degree of a first smooth surface M1 and a second smooth surface M2; determining a first pressure-bearing diameter d1 based on a first pressure-bearing area S1 corresponding to the breather valve in the closed position; determining the range of values ​​for a second pressure-bearing diameter d2 corresponding to the valve disc assembly in the maximum open position based on the mass m of the valve disc assembly, the maximum opening height H, the first pressure-bearing diameter d1, and the upper limit of impact energy E0; and setting the pressure profile of the valve disc assembly and / or the valve seat according to the range of values ​​for the second pressure-bearing diameter d2, so that the single reseating impact energy E when the valve disc assembly falls back from the maximum open position to the closed position does not exceed the upper limit of impact energy E0.

[0017] As a preferred embodiment of the design method of the metal-sealed breather valve of the present invention, the following steps are taken: based on the determined second pressure-bearing diameter d2, valve disc assembly mass m, and maximum opening height H, the single reseating impact energy E when the valve disc assembly falls back from the maximum opening position to the closed position is calculated, and the single reseating impact energy E is compared with the upper limit of impact energy E0; when E is greater than E0, the second pressure-bearing diameter d2, valve disc assembly mass m, and maximum opening height H are adjusted until E is not greater than E0.

[0018] The beneficial effects of this invention are as follows: By setting a sealing mating surface composed of a first smooth surface and a second smooth surface between the valve disc assembly and the valve seat, this invention improves the fitting accuracy of the valve disc assembly after reseating, thereby reducing the leakage of the breather valve and improving the sealing stability. At the same time, by coordinating the mass, maximum opening height, and second pressure diameter of the valve disc assembly, the impact energy of a single reseating when the valve disc assembly falls from the maximum opening position to the closed position does not exceed the upper limit of impact energy determined according to the allowable damage degree of the first and second smooth surfaces. This effectively reduces the impact damage to the smooth sealing surface when the valve disc assembly reseats, while ensuring the flow capacity of the breather valve, and slows down the generation of indentations, scratches, and wear, thereby improving the reliability and service life of repeated reseating of the sealing mating surface. Attached Figure Description

[0019] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments will be briefly introduced. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0020] Figure 1 This is a schematic diagram of the overall structure of the metal-sealed breather valve with controlled reseating impact energy according to the present invention.

[0021] Figure 2 This is a schematic diagram of the valve seat and valve disc assembly of the present invention when closed.

[0022] Figure 3 This is a schematic diagram of the valve seat and valve disc assembly of the present invention when it is open.

[0023] Figure 4 This is a schematic diagram of the maximum opening height of the present invention.

[0024] Figure 5 This is a schematic diagram of the guide section of the present invention.

[0025] Figure 6 This is a schematic diagram showing the correspondence between the first smooth surface and the second smooth surface of the present invention.

[0026] In the figure: 100, valve body; 200, valve seat; 300, valve disc assembly; 301, guide part; 302, pressure-bearing part; 303, weight-reducing part; M1, first smooth surface; M2, second smooth surface; S1, first pressure-bearing area; S2, second pressure-bearing area; d1, first pressure-bearing diameter; d2, second pressure-bearing diameter; m, mass; H, maximum opening height; E, single reseating impact energy; E0, upper limit of impact energy; J, reseating impact coefficient; J0, upper limit of preset reseating impact coefficient; Ra, surface roughness; g, gravitational acceleration. Detailed Implementation

[0027] To enable those skilled in the art to better understand the present invention, the present invention will be further described in detail below with reference to specific embodiments and accompanying drawings.

[0028] The terminology used in this invention is that which is currently widely used in the art in consideration of the function of the invention; however, these terms may vary according to the intent of those skilled in the art, precedent, or new technology in the art. Furthermore, specific terms may be chosen by the applicant, and in such cases, their detailed meanings will be described in the detailed description of the invention. Therefore, the terms used in this specification should not be construed as simple names, but rather based on their meanings and the overall description of the invention.

[0029] Example 1

[0030] Reference Figures 1-4 This embodiment provides a metal-sealed breather valve with controlled back-seating impact energy, including a valve body 100, a valve seat 200, and a valve disc assembly 300 that can move relative to the valve seat 200 between a closed position and a maximum open position. The valve body 100 is used to connect to a storage tank, container, or process pipeline and forms the main mounting structure of the breather valve; the valve seat 200 is located at the flow passage of the valve body 100 and provides a back-seating support position and sealing fit foundation for the valve disc assembly 300; the valve disc assembly 300 is located above the valve seat 200 and rises relative to the valve seat 200 when the pressure inside the tank reaches the opening condition to form a medium flow channel. After the pressure drops, it moves back towards the valve seat 200 and falls back to the closed position, thereby realizing the opening and closing cycle of the breather valve.

[0031] In this embodiment, a sealing mating surface is formed between the valve disc assembly 300 and the valve seat 200. This sealing mating surface includes a first smooth surface M1 and a second smooth surface M2. Specifically, the first smooth surface M1 and the second smooth surface M2 are respectively disposed at opposite mating portions in the valve seat 200 and the valve disc assembly 300. When the valve disc assembly 300 is in the closed position, the first smooth surface M1 and the second smooth surface M2 are in contact with each other to form a low-leakage sealing structure. Compared with structures using ordinary sealing rings or rough surface mating, the first smooth surface M1 and the second smooth surface M2 can form a higher precision surface contact or annular contact, thereby helping to reduce micro-leakage of the medium and improve the sealing stability after reseating. Preferably, the first smooth surface M1 and the second smooth surface M2 can be formed by precision machining, grinding, polishing, or other surface finishing methods to ensure good fitting accuracy during reseating. Of course, in this embodiment, the first smooth surface M1 and the second smooth surface M2 are not limited to absolute mirror contact; any smooth mating surface that can meet the low-leakage sealing requirements and achieve high reseating stability is applicable to this invention. For example, the first smooth surface M1 and the second smooth surface M2 can be mutually cooperating annular planar smooth surfaces; for example, the first smooth surface M1 and the second smooth surface M2 can be mutually cooperating annular conical smooth surfaces; for example, the first smooth surface M1 and the second smooth surface M2 can also be mutually cooperating arc smooth surfaces.

[0032] In this embodiment, the valve disc assembly 300 in the closed position corresponds to a first pressure-bearing region S1, the equivalent diameter of which is a first pressure-bearing diameter d1; the valve disc assembly 300 in the maximum open position corresponds to a second pressure-bearing region S2, the equivalent diameter of which is a second pressure-bearing diameter d2, and the second pressure-bearing diameter d2 is larger than the first pressure-bearing diameter d1. Here, the first pressure-bearing region S1 can be understood as the effective pressure-bearing range of the valve disc assembly 300 when it is in the closed state, subjected to the pressure of the medium inside the tank and used to overcome the self-weight of the valve disc assembly 300 or other closing forces; the second pressure-bearing region S2 can be understood as the effective pressure-bearing range of the valve disc assembly 300 after it rises to the maximum open position, where the medium pressure continues to act on the valve disc assembly 300. Since the pressure profile of the valve disc assembly 300 changes in different positions, the first pressure-bearing region S1 and the second pressure-bearing region S2 are not the same, and correspondingly, their first pressure-bearing diameter d1 and second pressure-bearing diameter d2 are also different. By setting the second pressure-bearing diameter d2 to be greater than the first pressure-bearing diameter d1, the pressure-bearing mechanical relationship can be changed after the valve disc assembly 300 is opened, providing a parameter basis for subsequent control of the reseating impact.

[0033] Furthermore, this embodiment does not achieve low-leakage sealing solely by setting the first smooth surface M1 and the second smooth surface M2, but rather by coordinating the mass m, maximum opening height H, and second pressure-bearing diameter d2 of the valve disc assembly 300. Here, the mass m of the valve disc assembly 300 can be understood as the total mass of the moving parts that participate in the lifting motion and generate inertia and impact during the descent; the maximum opening height H can be understood as the maximum lift of the valve disc assembly 300 when it moves from the closed position to the maximum opening position; and the second pressure-bearing diameter d2 reflects the pressure characteristics of the valve disc assembly 300 in the maximum opening state. By coordinating the design of the above three parameters, rather than simply pursuing the increase or decrease of a single parameter, the single reseating impact energy E of the valve disc assembly 300 when it falls from the maximum opening position to the closed position can be effectively controlled, while meeting the flow capacity requirements of the breather valve.

[0034] Specifically, in existing breather valves, to improve flow capacity, the maximum opening height H of the valve disc assembly is typically increased. However, increasing the maximum opening height H leads to an increased fall distance for the valve disc assembly 300, thereby increasing the impact risk during reseating. If the mass m of the valve disc assembly 300 is large, the impact on the valve seat 200 and the sealing mating surface during fall will also be correspondingly enhanced. If the second pressure-bearing diameter d2 is not designed properly, the pressure characteristics of the valve disc assembly 300 in the open state and the dynamic relationship during the fall process will become unbalanced, further exacerbating the reseating impact. Therefore, this embodiment achieves a predetermined flow capacity for the valve disc assembly 300 while ensuring that the reseating impact does not exceed the allowable range that the sealing mating surface can withstand.

[0035] In this embodiment, the single reseating impact energy E of the valve disc assembly 300 when it returns from the maximum open position to the closed position does not exceed the upper limit of impact energy E0. The upper limit of impact energy E0 is the upper limit of single reseating impact energy determined based on the allowable damage level of the first smooth surface M1 and the second smooth surface M2. E0 is not an arbitrary value, but an energy threshold determined by combining the acceptable degree of indentation, wear, scratches, plastic deformation, or sealing performance degradation of the first smooth surface M1 and the second smooth surface M2 during actual use. When the single reseating impact energy E of the valve disc assembly 300 when it reseats does not exceed the upper limit of impact energy E0, the first smooth surface M1 and the second smooth surface M2 can maintain good fitting accuracy and sealing performance within a predetermined number of opening and closing cycles, thereby balancing low leakage effect and long-term operational safety; conversely, if the single reseating impact energy E exceeds the upper limit of impact energy E0, the first smooth surface M1 and the second smooth surface M2 are more likely to accumulate damage during long-term repeated opening and closing, resulting in decreased reseating sealing performance, increased leakage, and even affecting the service life and operational safety of the breather valve.

[0036] For example, when the valve disc assembly 300 uses metal materials and is suitable for the corresponding Ga-level explosion-proof conditions, the upper limit of the single reseating impact energy E0 can be checked with reference to the corresponding limit values ​​in Table 1; under the premise of meeting the requirements for the degree of damage to the sealing surface, it is preferable to ensure that E0 does not exceed the single impact energy limit value under the corresponding conditions.

[0037] Table 1 shows the single-impact energy limit for Ga-level equipment.

[0038]

[0039] Therefore, the metal-sealed breather valve with controlled reseating impact energy provided in this embodiment not only improves the fitting accuracy and low leakage performance of the sealing mating surface by utilizing the first smooth surface M1 and the second smooth surface M2, but also controls the single reseating impact energy E of the valve disc assembly 300 within the upper limit E0 of the impact energy determined by the allowable damage degree of the smooth surface by coordinating the mass m, the maximum opening height H and the second pressure-bearing diameter d2 of the valve disc assembly 300. This effectively reduces the impact damage to the smooth sealing surface when the valve disc assembly 300 reseats, slows down the wear and failure of the sealing mating surface, improves the reseating reliability and overall service life, and is suitable for storage tanks, containers and related process equipment scenarios with high requirements for leakage control and safety.

[0040] Example 2

[0041] Reference Figure 2 , Figure 3 and Figure 4 In this embodiment, in order to quantitatively describe the impact effect when the valve disc assembly 300 falls back from the maximum open position to the closed position, the single reseating impact energy E satisfies the following formula: , Where g is the acceleration due to gravity.

[0042] Specifically, the above expression reflects the correspondence between the reseating impact energy of the valve disc assembly 300 and its mass m, maximum opening height H, and first and second pressure-bearing diameters d1 and d2 in this invention. In the formula, mass m represents the inertial basis of the valve disc assembly 300 during the reseating process; maximum opening height H represents the travel distance of the valve disc assembly 300 from the maximum open position to the closed position; and the first and second pressure-bearing diameters d1 and d2 respectively reflect the pressure characteristics of the valve disc assembly 300 in the closed and maximum open states. Through the combined effect of these parameters, the degree of a single impact on the sealing mating surface generated by the valve disc assembly 300 during the reseating process can be characterized relatively accurately, thus providing a clear basis for the coordinated design of low leakage and high safety performance in the breather valve.

[0043] In this embodiment, the terms in the above formula are: , The influence of the proportional relationship between the first pressure-bearing diameter d1 and the second pressure-bearing diameter d2 on the reseating impact energy E was characterized. When the second pressure-bearing diameter d2 increases relative to the first pressure-bearing diameter d1, the pressure characteristics of the valve disc assembly 300 in the maximum open state change, thereby affecting its dynamic process when it falls back from the maximum open position to the closed position. When the mass m of the valve disc assembly 300 increases or the maximum opening height H increases, the single reseating impact energy E will also increase accordingly. Therefore, in this invention, instead of optimizing a single parameter, the single reseating impact energy E is controlled within an allowable range through the coordinated matching of the mass m, the maximum opening height H, and the second pressure-bearing diameter d2.

[0044] Furthermore, the above formula also shows that the present invention does not merely adjust the structural parameters of the valve disc assembly 300 based on experience, but can design and verify the reseating impact through quantitative relationships. Specifically, in the design stage of the breather valve, the maximum opening height H of the valve disc assembly 300 can be determined first based on the expected flow capacity, and then its mass m can be determined by combining the structural form, material and size of the valve disc assembly 300. The first pressure diameter d1 and the second pressure diameter d2 can be determined based on the pressure profile of the valve disc assembly 300 in the closed position and the maximum open position. Then, the single reseating impact energy E of the valve disc assembly 300 during reseating can be calculated using the above formula. If the calculated single reseating impact energy E exceeds the upper limit E0 of the impact energy determined according to the allowable damage level of the first smooth surface M1 and the second smooth surface M2, it indicates that under the existing parameter matching, the valve disc assembly 300 may cause excessive impact damage to the first smooth surface M1 and the second smooth surface M2 during long-term opening and closing. In this case, optimization can be achieved by reducing the mass m of the valve disc assembly 300, reducing the maximum opening height H, and / or adjusting the second pressure-bearing diameter d2 until the single reseating impact energy E meets the design requirements.

[0045] In this embodiment, to more intuitively characterize the influence of the proportional relationship between the first pressure diameter d1 and the second pressure diameter d2 on the reseating impact degree of the valve disc assembly 300, the reseating impact coefficient J is defined as: , And the reseating impact coefficient J satisfies: , Wherein, J0 is the upper limit of the preset backseat impact coefficient.

[0046] Specifically, the reseating impact coefficient J is a dimensionless parameter determined by the proportional relationship between the first compression diameter d1 and the second compression diameter d2, and is used to reflect the influence degree of the change in the compression characteristics of the valve disc assembly 300 between the closed state and the maximum opening state on the reseating impact. Since the reseating impact coefficient J does not include specific dimension parameters such as mass m and maximum opening height H, it can more concentratedly characterize the influence law of the change in the compression area itself on the single reseating impact energy E. In this embodiment, the reseating impact coefficient J can be understood as a structural impact characterization parameter determined by the equivalent diameter relationship between the first compression area S1 and the second compression area S2.

[0047] Combined with the aforementioned single reseating impact energy formula, it can be seen that: .

[0048] Thus, when the mass m and the maximum opening height H of the valve disc assembly 300 are given, the larger the reseating impact coefficient J, the greater the single reseating impact energy E when the valve disc assembly 300 falls from the maximum opening position to the closed position; conversely, the smaller the reseating impact coefficient J, the smaller the single reseating impact energy E. Therefore, compared with only adjusting the structural dimensions by experience, in this embodiment, by introducing the reseating impact coefficient J, designers can more intuitively judge whether the change of the second compression diameter d2 relative to the first compression diameter d1 will cause the reseating impact to exceed the allowable range.

[0049] In this embodiment, the reseating impact coefficient J satisfies 0 < J ≤ J0. Among them, J > 0 indicates that the second compression diameter d2 is greater than the first compression diameter d1, that is, there is a difference in the compression characteristics of the valve disc assembly 300 at the maximum opening position and the compression characteristics at the closed position, so that the dynamic relationship during the reseating process changes; and J not being greater than the preset upper limit J0 of the reseating impact coefficient means that the impact increase introduced by the change in the compression area is limited within the allowable range. J0 is not an arbitrarily set value, but a coefficient upper limit comprehensively determined according to the allowable damage degree of the first smooth surface M1 and the second smooth surface M2, the sealing retention requirement within the predetermined opening and closing times, and the overall safety requirement of the breather valve. By making the reseating impact coefficient J not exceed J0, it is possible to avoid a significant increase in the reseating impact caused by setting the second compression diameter d2 too large, which is more conducive to protecting the mating integrity of the first smooth surface M1 and the second smooth surface M2.

[0050] Furthermore, the introduction of the reseating impact coefficient J facilitates the transformation of the design process of this invention from absolute dimensional control to proportional relationship control. Since the dimensions of the valve body 100, valve seat 200, and valve disc assembly 300 of different specifications of breather valves may vary significantly, it is difficult to establish a unified design standard among different specifications if only absolute pressure diameter values ​​are used for comparison. However, by using the reseating impact coefficient J, the proportional relationship between the first pressure diameter d1 and the second pressure diameter d2 can be used to uniformly evaluate the reseating impact level of breather valves of different specifications. In this embodiment, the reseating impact coefficient J is not only a calculation parameter but also an evaluation parameter that can be used for cross-specification design verification.

[0051] Therefore, this embodiment defines the reseating impact coefficient J and controls it within the preset upper limit J0 of the reseating impact coefficient, so that the proportional relationship between the first pressure-bearing diameter d1 and the second pressure-bearing diameter d2 can be clearly quantified and effectively constrained. This allows the valve disc assembly 300 to ensure flow capacity while avoiding increased reseating impact due to excessive changes in the pressure-bearing area. This, in turn, helps to improve the reliability of repeated reseating of the first smooth surface M1 and the second smooth surface M2, reduce leakage risk, and enhance the safety and stability of the breather valve during long-term operation.

[0052] Example 3

[0053] Reference Figure 2 , Figure 3 and Figure 4 In this embodiment, under the conditions that the first pressure diameter d1, the second pressure diameter d2, and the upper limit of impact energy E0 are determined, the mass m of the valve disc assembly 300 and the maximum opening height H satisfy the following: .

[0054] Specifically, the above relationship is a collaborative constraint relationship between mass m and maximum opening height H, obtained by further refining the formula for single reseating impact energy. This relationship is used to jointly limit the mass m and maximum opening height H of the valve disc assembly 300 when the first pressure diameter d1, the second pressure diameter d2, and the upper limit of impact energy E0 are already determined. In this embodiment, the mass m and maximum opening height H of the valve disc assembly 300 are not considered as independent parameters that can be arbitrarily adjusted separately, but rather are incorporated into a unified constraint framework as key variables that jointly affect the reseating impact energy E.

[0055] From the above relationship, it can be seen that, under the condition that the first compressive diameter d1 and the second compressive diameter d2 remain unchanged, the term is: , Since the coefficients are relatively fixed, the mass m of the valve disc assembly 300 and the maximum opening height H essentially satisfy a product constraint relationship. If the mass m of the valve disc assembly 300 increases, then to ensure that the single reseating impact energy E does not exceed the upper limit of impact energy E0, its allowable maximum opening height H should be reduced accordingly; conversely, if the maximum opening height H of the valve disc assembly 300 needs to be increased to improve the flow capacity of the breather valve, then the mass m of the valve disc assembly 300 should be reduced accordingly, or the ratio between the first pressure-bearing diameter d1 and the second pressure-bearing diameter d2 should be re-optimized. In this way, it is possible to avoid the loss of control over the reseating impact caused by focusing solely on the mass m or the maximum opening height H during the design process.

[0056] Furthermore, the constraint relationship in this embodiment is of great significance in solving the problem in the prior art of "simply increasing the opening height to improve flow rate, resulting in excessive reseating impact". In the design of a breather valve, the maximum opening height H is usually closely related to the flow capacity. Under similar conditions, an increase in the opening height H increases the flow area of ​​the annular gap, which is beneficial to improving the medium discharge or gas replenishment capacity. However, an increase in the maximum opening height H will increase the travel distance of the valve disc assembly 300 from the maximum open position to the closed position, thereby increasing the impact risk during reseating. If the mass m of the valve disc assembly 300 is also large, the impact will be further enhanced, which may easily lead to indentation, wear, or sealing performance degradation of the first smooth surface M1 and the second smooth surface M2 during long-term opening and closing. Therefore, this embodiment establishes a product constraint relationship between the mass m and the maximum opening height H, so that designers can simultaneously consider the lightweight design of the valve disc assembly 300 when pursuing improved flow capacity, thereby achieving structural optimization while ensuring the safety of reseating impact.

[0057] For example, in one design scenario, if the structure of the valve seat 200 of the breather valve is already determined, thus the first pressure-bearing diameter d1 is determined, and the second pressure-bearing diameter d2 is determined according to the pressure profile design, and the allowable damage level of the first smooth surface M1 and the second smooth surface M2 is determined to have an upper limit of impact energy E0, then the allowable combination range between the mass m of the valve disc assembly 300 and the maximum opening height H can be directly calculated using the above relationship. If the maximum opening height H set in the initial design to meet specific flow requirements is large, then the mass m of the valve disc assembly 300 should be reduced accordingly, for example, by optimizing the structural shape of the valve disc assembly 300, reducing the thickness of non-critical load-bearing areas, and selecting materials with lower specific gravity but meeting strength requirements for lightweight design; conversely, if the valve disc assembly 300 has a large mass m due to structural strength, corrosion resistance, or process requirements, then the maximum opening height H should be appropriately limited to prevent the valve disc assembly 300 from generating excessive single reseating impact energy E when it falls back.

[0058] The constraints in this embodiment can be used not only as verification formulas but also as a guiding basis for preliminary structural design. During design, the target flow capacity of the breather valve can be estimated based on the application conditions to initially determine the design range of the maximum opening height H. Then, the mass m of the valve disc assembly 300 is determined based on its structural scheme and material selection. Subsequently, the combination of the first pressure-bearing diameter d1, the second pressure-bearing diameter d2, and the upper limit of impact energy E0 is used to verify whether the combination of the mass m and the maximum opening height H meets the requirements. If not, the structure, material, pressure profile, or opening stroke of the valve disc assembly 300 can be readjusted until the constraints are met. Thus, this invention transforms the previously experience-based matching relationship between the mass m and the maximum opening height H into a calculable, comparable, and verifiable design relationship, enhancing the predictability and engineering operability of the breather valve design.

[0059] Example 4

[0060] Reference Figure 2 , Figure 3 and Figure 4 In this embodiment, in order to control the single reseating impact energy E of the valve disc assembly 300 when it falls from the maximum open position to the closed position within the upper limit of impact energy E0, the second pressure diameter d2 satisfies: .

[0061] Wherein, d1 is the equivalent diameter of the first pressure-bearing region S1, d2 is the equivalent diameter of the second pressure-bearing region S2, m is the mass of the valve disc assembly 300, g is the gravitational acceleration, H is the maximum opening height of the valve disc assembly 300, and E0 is the upper limit of impact energy determined according to the allowable damage level of the first smooth surface M1 and the second smooth surface M2.

[0062] Specifically, the aforementioned inequality is a constraint relationship for the second pressure-bearing diameter d2 derived from the aforementioned formula for single reseating impact energy and the reseating impact constraint conditions. Since this invention requires that the single reseating impact energy E of the valve disc assembly 300 falling from its maximum open position to its closed position not exceed the upper limit of impact energy E0, under the conditions that the mass m of the valve disc assembly 300, the maximum opening height H, and the first pressure-bearing diameter d1 are determined, the second pressure-bearing diameter d2 cannot be arbitrarily increased, but should meet the aforementioned range requirement. The second pressure-bearing diameter d2 is not only a geometric parameter characterizing the pressure characteristics of the valve disc assembly 300 in the open state, but also a key constraint parameter affecting whether the reseating impact energy E meets the design requirements.

[0063] Among them, the left side of the inequality This indicates that the second pressure-bearing diameter d2 is greater than the first pressure-bearing diameter d1, meaning that the second pressure-bearing area S2 corresponding to the valve disc assembly 300 in the maximum open position is larger than the first pressure-bearing area S1 in the closed position. This relationship is consistent with the design concept of the valve disc assembly 300 changing its pressure state after opening in this invention, and also provides a basis for introducing the reseating impact coefficient J. If the second pressure-bearing diameter d2 is not greater than the first pressure-bearing diameter d1, the difference in pressure characteristics between the valve disc assembly 300 in the open and closed states is insufficient, which is not conducive to realizing the coordinated design of the pressure profile in this invention.

[0064] The right-hand side of the inequality: .

[0065] This indicates that there is an upper limit to the value of the second pressure-bearing diameter d2. This upper limit is not an arbitrary empirical value, but is determined by the first pressure-bearing diameter d1, the mass m of the valve disc assembly 300, the maximum opening height H, and the upper limit of impact energy E0. Given that the permissible damage level of the first smooth surface M1 and the second smooth surface M2 is determined, i.e., the upper limit of impact energy E0 is determined, if the mass m of the valve disc assembly 300 is large, or the maximum opening height H is large, then to ensure that the single reseating impact energy E does not exceed the upper limit of impact energy E0, the permissible range of the second pressure-bearing diameter d2 needs to be more strictly limited; conversely, if the mass m of the valve disc assembly 300 is small, or the maximum opening height H is small, then the design range of the second pressure-bearing diameter d2 is relatively wider.

[0066] Therefore, this embodiment does not simply assume that the larger or smaller the second pressure-bearing diameter d2 is, the better. Instead, it emphasizes that the second pressure-bearing diameter d2 should be matched with the mass m and the maximum opening height H. Especially in the prior art, to improve the flow capacity of the breathing valve, there is often a tendency to increase the maximum opening height H of the valve disc assembly 300. However, when the maximum opening height H increases, the travel distance of the valve disc assembly 300 as it falls back to the closed position also increases accordingly. If a large second pressure-bearing diameter d2 is maintained, it is easier for the single reseating impact energy E to exceed the range allowed by the first smooth surface M1 and the second smooth surface M2. Therefore, this embodiment limits the upper limit of the second pressure-bearing diameter d2 to control the pressure profile of the valve disc assembly 300 in the maximum open state within a reasonable range, thereby preventing excessive reseating impact even when the valve disc assembly 300 meets a certain flow capacity requirement.

[0067] Furthermore, in the actual design process, the first pressure-bearing diameter d1 in the closed state can be determined first based on the structural form of the valve body 100 and valve seat 200. Then, the maximum opening height H of the valve disc assembly 300 can be determined based on the expected application scenario's requirements for the flow capacity of the breather valve. The mass m of the valve disc assembly 300 can then be determined by combining its material, dimensions, and structural form. Based on this, the upper limit of impact energy E0 is determined according to the allowable damage level of the first smooth surface M1 and the second smooth surface M2. Then, the allowable upper limit of the second pressure-bearing diameter d2 can be calculated using the aforementioned inequality. If the second pressure-bearing diameter d2 under the initial design exceeds this upper limit, it indicates that under the current parameter combination, the impact risk to the first smooth surface M1 and the second smooth surface M2 is high when the valve disc assembly 300 reseats. In this case, optimization should be performed by reducing the second pressure-bearing area S2, adjusting the pressure profile of the valve disc assembly 300, reducing the mass m of the valve disc assembly 300, or lowering the maximum opening height H, until the second pressure-bearing diameter d2 meets the aforementioned constraints.

[0068] Therefore, this embodiment, by providing a clear inequality range for the second pressure-bearing diameter d2, not only provides a calculable and verifiable basis for the pressure profile design of the valve disc assembly 300 in its maximum open position, but also unifies the mass m, maximum opening height H, first pressure-bearing diameter d1, and allowable damage level of the smooth sealing surface of the valve disc assembly 300 into the same design framework. This ensures low-leakage sealing performance of the first smooth surface M1 and the second smooth surface M2 while avoiding excessive reseating impact of the valve disc assembly 300 due to improper setting of the second pressure-bearing diameter d2, further improving the reliability, service life, and overall safety of the breather valve's reseating.

[0069] Example 5

[0070] Reference Figure 3 In this embodiment, both the first smooth surface M1 and the second smooth surface M2 are metal sealing surfaces. The upper limit of impact energy E0 is the upper limit of single reseating impact energy allowed when the first smooth surface M1 and the second smooth surface M2 maintain a predetermined sealing performance within a predetermined number of opening and closing cycles.

[0071] In this invention, both the first smooth surface M1 and the second smooth surface M2 are metal sealing surfaces, which fit together to form a metal-to-metal sealing fit after the valve disc assembly reseated. By making both the first smooth surface M1 and the second smooth surface M2 metal surfaces, the wear resistance, corrosion resistance, and sealing stability of the sealing pair under high temperature, high pressure, and complex working conditions can be improved, and the risk of leakage caused by aging, deformation, or failure of non-metallic sealing materials can be reduced. Since metal sealing surfaces are more sensitive to impact loads, excessive reseating impact energy can easily cause damage to the sealing surface and affect the subsequent sealing effect. Therefore, this invention designs and controls the upper limit E0 of the single reseating impact energy to ensure that the metal sealing pair still has good sealing stability and reliability under multiple opening and closing conditions.

[0072] Specifically, the upper limit of impact energy E0 in this embodiment is not an arbitrarily set empirical value, nor is it an abstract parameter introduced simply to satisfy the calculation formula. Rather, it is a functional design parameter that directly corresponds to the actual service life, allowable damage level, and sealing performance requirements of the first smooth surface M1 and the second smooth surface M2. The determination of the upper limit of impact energy E0 is based on the fact that during the repeated opening and closing of the breather valve, the single reseating impact generated when the valve disc assembly 300 falls from the maximum open position to the closed position should not cause the first smooth surface M1 and the second smooth surface M2 to produce indentations, wear, scratches, plastic deformation, or instability of the mating surfaces within a predetermined number of opening and closing cycles, thereby ensuring that both can maintain the predetermined sealing performance after multiple reseating cycles.

[0073] The predetermined number of opening and closing cycles can be determined based on the application scenario, design life, opening and closing frequency, and maintenance cycle of the breather valve. For example, in the scenario of breather control for storage tanks with a high opening and closing frequency, a larger number of cycles of opening and closing can be used as the predetermined number of opening and closing cycles; in the scenario of a relatively low opening and closing frequency but with high requirements for sealing safety, the predetermined number of opening and closing cycles can also be determined based on a combination of operating cycle and maintenance cycle. The predetermined sealing performance can be understood as the ability of the first smooth surface M1 and the second smooth surface M2 to maintain a predetermined sealing fit and allowable leakage level after reaching the predetermined number of opening and closing cycles, that is, the breather valve can still meet the set low leakage requirements and safety requirements after long-term operation.

[0074] To more specifically illustrate the basis for determining the upper limit of impact energy E0, this embodiment conducts simulation analysis on the evolution of surface roughness Ra of the first smooth surface M1 and the second smooth surface M2 under repeated reseating impact for different application scenarios.

[0075] In this embodiment, in the initial state, the surface roughness of the first smooth surface M1 and the second smooth surface M2 is set to Ra0 = 0.032 μm, and the surface roughness increment ΔRa = Ran - Ra0 is used as an evaluation index to characterize the degree of impact damage accumulation of the smooth sealing surface, where Ran is the surface roughness after n reseating impacts.

[0076] In tank breathing control scenarios with high opening and closing frequencies, the breather valve is in a state of frequent opening and closing for extended periods. The first smooth surface M1 and the second smooth surface M2 are more prone to damage accumulation due to repeated reseating impacts. Therefore, in this scenario, it is necessary not only to examine the influence of different single reseating impact energies E on surface roughness Ra, but also to consider the cumulative effect of the number of impacts N on surface roughness Ra under the same single reseating impact energy. Simulations of this scenario yielded the following results: Table 2: Effect of different single-impact reseating energies E on surface roughness Ra under a fixed number of impacts (high-frequency scenario simulation).

[0077]

[0078] As shown in Table 2, in high-frequency opening and closing scenarios, when the impact energy E of a single reseating event does not exceed 3.2 J, the surface roughness of the first smooth surface M1 and the second smooth surface M2 increases relatively slowly, and the average roughness remains at a low level. When E reaches 3.5 J or higher, the roughness increases significantly, indicating that the damage to the smooth sealing surface has entered an accelerated accumulation stage. Therefore, in this scenario, the upper limit of the impact energy E0 is preferably set to 3.0 J to 3.2 J, more preferably 3.0 J.

[0079] Furthermore, taking the preferred single-impact energy of E = 3.0 J, the surface roughness Ra of the first smooth surface M1 and the second smooth surface M2 under different impact numbers N was simulated, and the following results were obtained: Table 3: Effect of impact number N on surface roughness Ra under optimal single-impact energy (high-frequency scenario simulation).

[0080]

[0081] As shown in Table 3, in high-frequency opening and closing scenarios, even if the single reseating impact energy E is controlled at the preferred value of 3.0J, the surface roughness Ra of the first smooth surface M1 and the second smooth surface M2 will still gradually increase as the number of impacts N increases. However, the growth trend is relatively slow, and it can maintain good sealing performance over a longer period of time.

[0082] In scenarios with relatively low opening and closing frequencies but high sealing safety requirements, media leakage control is more sensitive. Therefore, stricter constraints are needed on the surface roughness variations of the first smooth surface M1 and the second smooth surface M2. Even with relatively few impacts, a lower upper limit for impact energy E0 should be preferred. Simulations of this scenario yielded the following results: Table 4: Effect of different single reseating impact energies E on surface roughness Ra under a fixed number of impacts (simulation of high sealing safety scenario).

[0083]

[0084] As shown in Table 4, in low-frequency but high-sealing-safety-requirement scenarios, when the single reseating impact energy E does not exceed 2.4J, the surface roughness increase of the first smooth surface M1 and the second smooth surface M2 is relatively small, and the sealing state is relatively stable. When E reaches 2.8J or above, the roughness increment increases significantly, making it more likely to affect sealing safety. Therefore, in this scenario, the upper limit of impact energy E0 is preferably set to 2.0J~2.4J, more preferably 2.2J.

[0085] Furthermore, taking the preferred single-impact energy of E = 2.2 J, the surface roughness Ra of the first smooth surface M1 and the second smooth surface M2 under different impact numbers N was simulated, and the following results were obtained: Table 5: Effect of impact number N on surface roughness Ra under optimized single reseating impact energy (simulation of high sealing safety scenario).

[0086]

[0087] As shown in Table 5, in low-frequency but high-sealing-safety-requirement scenarios, when the single reseating impact energy E is 2.2J, the surface roughness of the first smooth surface M1 and the second smooth surface M2 increases very gradually, which can better meet the application requirements for high sealing stability.

[0088] Based on the simulation results above, it can be seen that both the single reseating impact energy E and the number of impacts N affect the surface roughness Ra of the first smooth surface M1 and the second smooth surface M2, and there is a clear coupling relationship between the two: when the number of impacts N is constant, the larger the single reseating impact energy E is, the greater the increase in surface roughness Ra; when the single reseating impact energy E is constant, as the number of impacts N increases, the surface roughness Ra gradually accumulates and increases.

[0089] Therefore, in tank breathing control scenarios with high opening and closing frequencies, to balance flow capacity and long-term lifespan, the upper limit of impact energy E0 is preferably 3.0J to 3.2J, more preferably 3.0J; in scenarios with relatively low opening and closing frequencies but high sealing safety requirements, to prioritize ensuring the long-term stability of the sealing mating surfaces, the upper limit of impact energy E0 is preferably 2.0J to 2.4J, more preferably 2.2J. Thus, the determination of the upper limit of impact energy E0 in this embodiment is not only related to the allowable damage level of the first smooth surface M1 and the second smooth surface M2, but also to the opening and closing frequency and sealing safety requirements in the specific application scenario; by controlling the single reseating impact energy E and its cumulative effect, the first smooth surface M1 and the second smooth surface M2 can maintain the predetermined sealing performance within a predetermined number of opening and closing cycles.

[0090] Example 6

[0091] Reference Figure 3 In this embodiment, the surface roughness Ra of the first smooth surface M1 and the second smooth surface M2 is no greater than 0.1 μm.

[0092] Specifically, the first smooth surface M1 and the second smooth surface M2 constitute the key sealing mating surfaces between the valve disc assembly 300 and the valve seat 200. The surface conditions of these two surfaces directly affect the degree of fit, contact uniformity, and leakage control effect after reseating. If the surface roughness of the first smooth surface M1 and the second smooth surface M2 is too large, although they can contact each other in the closed position, there are still many microscopic peak and valley structures in their contact interface, resulting in local contact discontinuity, a reduction in the actual contact area, and the formation of potential leakage channels in the microscopic depression areas, thereby affecting the low leakage performance of the breather valve. Therefore, in this embodiment, the surface roughness Ra of the first smooth surface M1 and the second smooth surface M2 is controlled to be no greater than 0.1 μm, so that they can form a more uniform and stable contact state when reseating.

[0093] In this embodiment, a surface roughness Ra of no more than 0.1 μm means that the first smooth surface M1 and the second smooth surface M2 have a high degree of surface finish, with small micro-undulations, which is beneficial to improving the surface contact quality between them. This reduces stress concentration caused by localized high-point contact, preventing the sealing mating surface from bearing concentrated loads only at a few protrusions when the valve disc assembly 300 reseated. Furthermore, it increases the actual contact area between the first smooth surface M1 and the second smooth surface M2, allowing for good sealing even with minimal reseating deformation. Therefore, the leakage of the breather valve in the closed state can be effectively controlled, and stable sealing performance is more easily maintained during repeated opening and closing.

[0094] Furthermore, limiting the surface roughness Ra of the first smooth surface M1 and the second smooth surface M2 to no more than 0.1 μm can also create a synergistic effect with the aforementioned impact energy control scheme. This invention does not simply rely on high-precision machining of the smooth surfaces to reduce leakage, nor does it solely rely on the synergistic design of mass m, maximum opening height H, and second pressure diameter d2 to reduce reseating impact. Instead, it combines both: by controlling the surface roughness Ra, the first smooth surface M1 and the second smooth surface M2 achieve high fitting accuracy during reseating; simultaneously, by controlling the single reseating impact energy E to not exceed the upper limit of impact energy E0, the damage to the aforementioned high-precision smooth surfaces caused by reseating impact is reduced. Therefore, the situation where "although the sealing surface has high machining precision, it is rapidly damaged due to excessive reseating impact" can be avoided, thus better maintaining the sealing stability of the smooth surface during long-term opening and closing processes.

[0095] In practical implementation, the first smooth surface M1 and the second smooth surface M2 can be formed by turning, grinding, lapping, polishing, ultra-precision machining, or other surface finishing processes to achieve a surface roughness Ra of no more than 0.1 μm. Preferably, the portion of the valve seat 200 where the first smooth surface M1 is formed can be an annular sealing contact area, and the portion of the valve disc assembly 300 where the second smooth surface M2 is formed can be a corresponding annular sealing contact area. Thus, when the valve disc assembly 300 falls back and closes, a circumferentially continuous sealing fit can be formed between the first smooth surface M1 and the second smooth surface M2, thereby further reducing the risk of leakage. Of course, this embodiment does not limit the first smooth surface M1 and the second smooth surface M2 to be formed using the same process; as long as both ultimately meet the surface roughness requirements and the sealing fit requirements, they are applicable to this invention.

[0096] Example 7

[0097] Reference Figure 3 and Figure 5 In this embodiment, the valve disc assembly 300 includes a guide portion 301, which is used to limit the sway of the valve disc assembly 300 during the process of falling back from the maximum open position to the closed position, so that the first smooth surface M1 and the second smooth surface M2 return to the center.

[0098] Specifically, during the process of the valve disc assembly 300 returning from the maximum open position to the closed position, it does not simply move in a perfectly vertical straight line along the ideal central axis. In actual operation, due to factors such as media flow disturbance, the distribution of the valve disc assembly 300's own center of gravity, structural assembly deviations, uneven local stress, and changes in the internal flow field of the valve body 100, the valve disc assembly 300 may experience a certain degree of lateral offset, tilting oscillation, or circumferential sway during the return process. If the above sway is not effectively limited, when the valve disc assembly 300 reseated, localized initial contact, eccentric contact, or oblique contact may easily occur between the first smooth surface M1 and the second smooth surface M2, resulting in uneven contact pressure distribution, localized stress concentration, and amplified reseating impact. This is not only detrimental to the stable fit of the sealing surfaces but also more likely to form indentations, scratches, and uneven wear on the first smooth surface M1 and the second smooth surface M2, thereby affecting the low leakage performance and long service life of the breather valve.

[0099] Therefore, this embodiment provides a guide portion 301 on the valve disc assembly 300 to constrain the lifting and lowering trajectory of the valve disc assembly 300, ensuring that it maintains high axial consistency and posture stability throughout its return from the maximum open position to the closed position. Specifically, the guide portion 301 can be used to guide and limit the movement direction of the valve disc assembly 300, reducing its lateral degrees of freedom during the return process, allowing the valve disc assembly 300 to return to its seat in a manner closer to axial alignment when approaching the valve seat 200. Consequently, when the valve disc assembly 300 returns to the closed position, the first smooth surface M1 and the second smooth surface M2 can contact each other in a more uniform and synchronous manner, thereby improving the reseating alignment and repeatability accuracy of the sealing mating surfaces.

[0100] In practical implementation, the guide section 301 can be configured as a guide structure that cooperates with the valve body 100, valve seat 200, or other fixed structures, such as a guide rod, guide column, guide sleeve, guide hole, guide flange, guide ring, or other structural forms that can constrain the movement direction of the valve disc assembly 300. The specific guide form adopted can be selected according to the size specifications of the breather valve, the installation method, the opening and closing stroke, and the manufacturing and assembly conditions. The key is to reduce the sway and improve the reseating alignment of the valve disc assembly 300 during the retraction process.

[0101] Example 8

[0102] Reference Figure 6 In this embodiment, the valve disc assembly 300 includes a pressure-receiving part 302 and a weight-reducing part 303. A second smooth surface M2 is formed on the pressure-receiving part 302, and the weight-reducing part 303 is provided with a region that avoids overlapping with the second smooth surface M2.

[0103] Specifically, in this embodiment, the valve disc assembly 300 not only needs to form a stable sealing fit with the valve seat 200 when reseating, but also needs to have a reasonable mass distribution during opening and closing to balance flow capacity, reseating impact control, and seal life requirements. To this end, the valve disc assembly 300 can be divided into a pressure-bearing part 302 that bears the main pressure and sealing fit functions, and a weight-reducing part 303 for reducing overall mass. The pressure-bearing part 302 is mainly used to form the effective pressure profile of the valve disc assembly 300 in the closed position and the maximum open position, and to form a second smooth surface M2 at its mating position opposite to the valve seat 200, thereby ensuring that the valve disc assembly 300 can form a high-precision sealing fit with the first smooth surface M1 when it falls back to the closed position.

[0104] In this embodiment, the weight-reducing part 303 is positioned to avoid the area overlapping with the second smooth surface M2. In other words, the weight-reducing part 303 is positioned to avoid the key sealing and mating area forming the second smooth surface M2, so that the valve disc assembly 300 can achieve weight reduction without compromising the sealing and mating function and pressure profile stability of the corresponding area of ​​the second smooth surface M2. Through this arrangement, on the one hand, the overall mass m of the valve disc assembly 300 can be reduced, thereby helping to reduce the inertial effect and single reseating impact energy E when the valve disc assembly 300 falls back from the maximum open position to the closed position; on the other hand, it can maintain good flatness, strength and rigidity in the area where the second smooth surface M2 is located, so that it can maintain high fitting accuracy and reseating stability when mating with the first smooth surface M1.

[0105] In practical implementation, the weight-reducing part 303 can be configured as a thinning region, a groove region, a hollow region, a lightweight cavity, or other structural forms that help reduce weight, depending on the structural form of the valve disc assembly 300. As long as the weight-reducing part 303 does not coincide with the second smooth surface M2 and does not significantly weaken the pressure-bearing function and sealing stability of the pressure-bearing part 302, it can be applied to the present invention. For example, in one embodiment, the pressure-bearing part 302 can be located on the side of the valve disc assembly 300 near the valve seat 200 and form an annular sealing area, with the second smooth surface M2 disposed on the annular sealing area; the weight-reducing part 303 can be disposed on the side of the pressure-bearing part 302 away from the second smooth surface M2, or disposed in the non-sealing contact area around the pressure-bearing part 302, so as to reduce the weight of the valve disc assembly 300 by local thinning or local material removal. For example, in another embodiment, the weight reduction part 303 may be provided in the non-critical load-bearing area of ​​the valve disc assembly 300 in the middle or at the edge, and weight reduction may be achieved by providing annular grooves, radial grooves or multiple distributed weight reduction holes.

[0106] Furthermore, the partitioning arrangement of the pressure-bearing part 302 and the weight-reducing part 303 in this embodiment can also coordinate with the aforementioned design of mass m, maximum opening height H, and second pressure-bearing diameter d2. The aforementioned embodiments have shown that the mass m of the valve disc assembly 300 is one of the important parameters affecting the single reseating impact energy E. With the first pressure-bearing diameter d1, the second pressure-bearing diameter d2, and the upper limit of impact energy E0 determined, appropriately reducing the mass m of the valve disc assembly 300 allows for greater adjustment space for setting the maximum opening height H while ensuring that the impact energy E does not exceed the upper limit of impact energy E0. Therefore, by setting the weight-reducing part 303 in an area that does not affect the stability of the second smooth surface M2 and the pressure-bearing part 302, the valve disc assembly 300 can be lightweighted without sacrificing sealing performance, thus better balancing the flow capacity and reseating safety of the breather valve.

[0107] Therefore, this embodiment, by providing a pressure-bearing portion 302 and a weight-reducing portion 303 on the valve disc assembly 300, and by forming the second smooth surface M2 on the pressure-bearing portion 302 and setting the weight-reducing portion 303 in a region that avoids overlapping with the second smooth surface M2, enables the valve disc assembly 300 to achieve a lightweight design while possessing good sealing fit and pressure profile stability. This not only reduces the mass m of the valve disc assembly 300 and decreases the reseating impact energy E, but also avoids interference of the weight-reducing structure with the sealing function of the second smooth surface M2, thereby further improving the low-leakage performance, reseating reliability, and overall operational safety of the breather valve.

[0108] Example 9

[0109] This embodiment also provides a design method for a metal-sealed breather valve. This method is used to collaboratively design the sealing structure, pressure profile, and reseating impact parameters between the valve disc assembly 300 and the valve seat 200 in the breather valve, so that the breather valve meets low-leakage sealing requirements while also ensuring reseating safety and long-term operational reliability. The specific design method includes the following steps: First, the upper limit of impact energy E0 is determined based on the permissible damage level of the first smooth surface M1 and the second smooth surface M2. Specifically, in this embodiment, the first smooth surface M1 and the second smooth surface M2 constitute the key sealing mating surfaces of the breather valve, and they will continuously withstand the impact of the valve disc assembly 300 reseating during repeated opening and closing. To prevent the first smooth surface M1 and the second smooth surface M2 from developing indentations, wear, scratches, plastic deformation, or a decrease in sealing performance beyond the permissible range due to impact accumulation within a predetermined number of opening and closing cycles, it is necessary to pre-determine an energy threshold that reflects the tolerance of the smooth sealing surfaces, namely the upper limit of impact energy E0. The upper limit of impact energy E0 is the basic parameter for subsequent design and verification of the mass m of the valve disc assembly 300, the maximum opening height H, and the second pressure-bearing diameter d2. Its corresponding design objective is that after long-term opening and closing operation of the valve disc assembly 300, the first smooth surface M1 and the second smooth surface M2 can still maintain the predetermined sealing performance.

[0110] Secondly, the first pressure-bearing diameter d1 is determined based on the first pressure-bearing area S1 corresponding to the breather valve in the closed position. Specifically, when the breather valve is closed, the valve disc assembly 300 and the valve seat 200 are in contact with each other, and the effective pressure range of the medium pressure acting on the valve disc assembly 300 constitutes the first pressure-bearing area S1. Since the first pressure-bearing area S1 is directly related to the structural contours of the valve body 100, the valve seat 200, and the valve disc assembly 300 in the closed state, the range of the first pressure-bearing area S1 can be determined during the design process based on the sealing opening structure of the valve seat 200, the contact contour of the valve disc assembly 300, and the medium action area, and then the first pressure-bearing area S1 can be further converted into the first pressure-bearing diameter d1. This first pressure-bearing diameter d1 is an important basic parameter for subsequently determining the second pressure-bearing diameter d2 and calculating the reseating impact coefficient J and the single reseating impact energy E.

[0111] Then, based on the mass m, maximum opening height H, first pressure diameter d1, and upper limit of impact energy E0 of the valve disc assembly 300, the range of values ​​for the second pressure diameter d2 corresponding to the maximum opening position of the valve disc assembly 300 is determined. In this embodiment, instead of arbitrarily assigning the second pressure diameter d2 and then passively checking whether it meets the reseating impact requirement, the upper limit of impact energy E0 is directly used as the design target, the first pressure diameter d1 as the structural reference, and the mass m and maximum opening height H of the valve disc assembly 300 are comprehensively considered to deduce the allowable range of the second pressure diameter d2 in reverse. In this way, the second pressure diameter d2 is no longer an isolated parameter selected based on experience, but becomes a design parameter constrained by low leakage requirements, the allowable damage level of the smooth surface, and reseating safety requirements. In this way, the design source can avoid setting the second pressure diameter d2 too large, which would cause the single reseating impact energy E of the valve disc assembly 300 falling from the maximum opening position to the closed position to exceed the upper limit of impact energy E0.

[0112] Furthermore, the pressure profiles of the valve disc assembly 300 and / or the valve seat 200 are set according to the range of the second pressure diameter d2, so that the single reseating impact energy E when the valve disc assembly 300 falls from the maximum open position to the closed position does not exceed the upper limit of impact energy E0. Specifically, the second pressure region S2 of the valve disc assembly 300 in the maximum open position and its corresponding second pressure diameter d2 are essentially determined by the relative structural profiles of the valve disc assembly 300 and the valve seat 200 in the open state. Therefore, in this embodiment, the second pressure region S2 can be set by adjusting the shape of the pressure portion 302 of the valve disc assembly 300, the pressure profile boundary, the size of the local pressure surface, and / or by adjusting the shape and range of the corresponding mating area of ​​the valve seat 200, so that its corresponding second pressure diameter d2 falls within the allowable range. Thus, the dynamic characteristics of the valve disc assembly 300 when falling from the maximum open position to the closed position can be controlled within the expected range, thereby ensuring that the single reseating impact energy E does not exceed the upper limit of impact energy E0.

[0113] In this embodiment, the design method described above does not simply optimize a single parameter in isolation. Instead, it incorporates multiple factors, such as the allowable damage level of the first smooth surface M1 and the second smooth surface M2, the first pressure-bearing diameter d1, the second pressure-bearing diameter d2, the mass m of the valve disc assembly 300, and the maximum opening height H, into the same design chain, forming a complete design logic from "sealing life requirements" to "impact energy targets" and then to "pressure profile design." This ensures that the first smooth surface M1 and the second smooth surface M2 have good low-leakage sealing performance. Furthermore, by reasonably matching the pressure profile and motion parameters, the impact of the valve disc assembly 300 during reseating can be effectively controlled, preventing rapid damage to the high-precision smooth surface due to excessive impact.

[0114] Therefore, this embodiment provides a design method for a metal-sealed breather valve, which allows the valve's structural design to move beyond traditional empirical adjustments. Instead, it enables a systematic design based on the permissible damage level of the smooth sealing surface and the upper limit of impact energy E0, combined with the first pressure-bearing diameter d1, the mass m of the valve disc assembly 300, the maximum opening height H, and the second pressure-bearing diameter d2. This ensures low leakage performance while effectively reducing impact damage to the first smooth surface M1 and the second smooth surface M2 during valve disc assembly 300 reseating, thereby improving the overall safety, reseating reliability, and long-term service life of the breather valve.

[0115] Example 10

[0116] In this embodiment, the design method further includes the following verification and adjustment steps: based on the determined second pressure diameter d2, the mass m of the valve disc assembly 300, and the maximum opening height H, calculate the single reseating impact energy E when the valve disc assembly 300 falls back from the maximum opening position to the closed position, and compare the single reseating impact energy E with the upper limit of impact energy E0; when E is greater than E0, adjust the second pressure diameter d2, the mass m of the valve disc assembly 300, and the maximum opening height H until E is not greater than E0.

[0117] In this embodiment, the single reseating impact energy E can be calculated according to the aforementioned formula. Specifically, given that the first pressure diameter d1, the second pressure diameter d2, the mass m of the valve disc assembly 300, and the maximum opening height H are determined, the single reseating impact energy E when the valve disc assembly 300 falls from the maximum opening position to the closed position can be obtained using the corresponding energy formula. This calculation result reflects the impact level acting on the first smooth surface M1 and the second smooth surface M2 when the valve disc assembly 300 reseats under the current structure and parameter combination. Subsequently, by comparing the calculated single reseating impact energy E with the upper limit of impact energy E0 determined according to the allowable damage level of the first smooth surface M1 and the second smooth surface M2, it can be determined whether the current design meets the predetermined sealing life and safety requirements.

[0118] If the calculation result satisfies that E is not greater than E0, it indicates that under the current parameter combination, the impact level of the valve disc assembly 300 when it falls back from the maximum open position to the closed position is within the allowable range of the first smooth surface M1 and the second smooth surface M2. Within the predetermined number of opening and closing cycles, the accumulated damage to the first smooth surface M1 and the second smooth surface M2 caused by repeated reseating impacts will not exceed the allowable level, and the breather valve can maintain the predetermined sealing performance well. At this time, the combination of the second pressure-bearing diameter d2, the mass m of the valve disc assembly 300, and the maximum opening height H can be used as the parameter combination that meets the design requirements.

[0119] Conversely, if the calculation results show that E is greater than E0, it indicates that under the current design parameters, the single impact energy during the reseating of the valve disc assembly 300 exceeds the damage threshold allowed by the first smooth surface M1 and the second smooth surface M2. If this set of parameters continues to be used, with the increase in the number of opening and closing of the breather valve, the first smooth surface M1 and the second smooth surface M2 are more prone to problems such as deeper indentations, increased local wear, unstable mating surfaces, decreased sealing fit, and increased leakage, making it difficult to achieve the low leakage and high safety performance required by this invention. Therefore, this embodiment requires that when E is greater than E0, at least one of the second pressure-bearing diameter d2, the mass m of the valve disc assembly 300, and the maximum opening height H be adjusted until E is not greater than E0.

[0120] Specifically, during the adjustment process, the second pressure-bearing diameter d2, the mass m of the valve disc assembly 300, and the maximum opening height H can be optimized individually or in combination according to actual design requirements. For example, by adjusting the pressure profile of the valve disc assembly 300 and / or the valve seat 200, the second pressure-bearing diameter d2 corresponding to the second pressure-bearing area S2 can be reduced, thereby lowering the reseating impact level caused by changes in pressure characteristics. Alternatively, the mass m of the valve disc assembly 300 can be reduced by optimizing the structural layout, material selection, or local weight reduction scheme, thus reducing the inertial basis during the fall-back process. Furthermore, by rematching the flow capacity and opening stroke of the breather valve, the maximum opening height H can be appropriately reduced to shorten the movement path of the valve disc assembly 300 from the maximum opening position to the closed position, thereby reducing the single reseating impact energy E. In practical applications, the adjustment of the above parameters is not limited to individual adjustments; they can usually be jointly optimized according to the breather valve specifications, operating conditions, and manufacturing conditions to ensure that E ultimately does not exceed E0 while meeting the requirements for flow capacity, sealing performance, and structural strength.

[0121] Finally, it should be noted that the methods and devices described in detail above are merely embodiments, and those skilled in the art can modify these embodiments in different ways as long as they do not depart from the scope of the present invention.

Claims

1. A metal-sealed breather valve with controlled back-seating impact energy, comprising a valve body (100), a valve seat (200), and a valve disc assembly (300) movable relative to the valve seat (200) between a closed position and a maximum open position, characterized in that: A sealing mating surface is formed between the valve disc assembly (300) and the valve seat (200), the sealing mating surface including a first smooth surface (M1) and a second smooth surface (M2). The valve disc assembly (300) in the closed position corresponds to a first pressure-bearing area (S1), the equivalent diameter of the first pressure-bearing area (S1) is a first pressure-bearing diameter d1, and the valve disc assembly (300) in the maximum open position corresponds to a second pressure-bearing area (S2), the equivalent diameter of the second pressure-bearing area (S2) is a second pressure-bearing diameter d2, and the second pressure-bearing diameter d2 is greater than the first pressure-bearing diameter d1; The mass m, maximum opening height H, and second pressure diameter d2 of the valve disc assembly (300) are coordinated to ensure that the single reseating impact energy E when the valve disc assembly (300) falls from the maximum opening position to the closed position is not greater than the upper limit of impact energy E0. The upper limit of impact energy E0 is the upper limit of single reseating impact energy determined according to the allowable damage degree of the first smooth surface (M1) and the second smooth surface (M2). The single-cycle recoil impact energy E satisfies the following equation: ， Where g is the acceleration due to gravity; Given the first pressure diameter d1, the second pressure diameter d2, and the upper limit of impact energy E0, the mass m of the valve disc assembly (300) and the maximum opening height H satisfy the following: ， The second pressure-bearing diameter d2 satisfies: ， Both the first smooth surface (M1) and the second smooth surface (M2) are metal sealing surfaces; Wherein, the upper limit of impact energy E0 is the upper limit of single reseating impact energy allowed to maintain the predetermined sealing performance of the first smooth surface (M1) and the second smooth surface (M2) within a predetermined number of opening and closing cycles; The surface roughness Ra of both the first smooth surface (M1) and the second smooth surface (M2) is no greater than 0.1 μm; The valve disc assembly (300) includes a pressure-receiving part (302) and a weight-reducing part (303). The second smooth surface (M2) is formed on the pressure-receiving part (302), and the weight-reducing part (303) is disposed in the valve disc assembly (300) in a region other than the projection area of ​​the second smooth surface (M2).

2. The metal-sealed breather valve with controlled reseating impact energy as described in claim 1, characterized in that: The valve disc assembly (300) includes a guide (301) for limiting the sway of the valve disc assembly (300) during its return from the maximum open position to the closed position, so as to align the first smooth surface (M1) and the second smooth surface (M2).

3. A design method for a metal-sealed breather valve, characterized in that: The application to the metal-sealed breather valve with controlled reseating impact energy as described in claim 2 further includes the following steps: The upper limit of impact energy E0 is determined based on the permissible damage level of the first smooth surface (M1) and the second smooth surface (M2); The first pressure diameter d1 is determined based on the first pressure zone (S1) corresponding to the closed position of the breathing valve; Based on the mass m, maximum opening height H, first pressure diameter d1, and upper limit of impact energy E0 of the valve disc assembly (300), determine the range of values ​​for the second pressure diameter d2 corresponding to the maximum opening position of the valve disc assembly (300). The pressure profile of the valve disc assembly (300) and / or valve seat (200) is set according to the range of the second pressure diameter d2, so that the single reseating impact energy E when the valve disc assembly (300) falls back from the maximum open position to the closed position is not greater than the upper limit of the impact energy E0.

4. The design method of the metal-sealed breather valve as described in claim 3, characterized in that: Based on the determined second pressure diameter d2, the mass m of the valve disc assembly (300) and the maximum opening height H, calculate the single reseating impact energy E when the valve disc assembly (300) falls back from the maximum opening position to the closed position, and compare the single reseating impact energy E with the upper limit of impact energy E0. When E is greater than E0, adjust the second pressure-bearing diameter d2, the mass m of the valve disc assembly (300), and the maximum opening height H until E is not greater than E0.

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