Breather valve with thermal jacket and method for determining target flow-through thickness thereof

Abstract

The present application relates to the technical field of breathing valve heat preservation, and particularly relates to a breathing valve with a heat preservation jacket and a target flow thickness determination method thereof, which comprises a valve body in which a valve cavity is formed; a heat preservation jacket arranged outside the valve body and forming a heating medium flow cavity with the valve body; wherein the heating medium flow cavity extends along the outer wall of the valve body, and the heating medium flow cavity has a consistent target flow thickness D in the extension direction thereof. The present application can make the temperature of the valve cavity not lower than the target heat preservation temperature at a preset heating medium temperature by forming the heating medium flow cavity extending along the outer wall of the valve body outside the valve body and making the heating medium flow cavity have a consistent target flow thickness in the extension direction thereof. Thus, the heating medium can continuously supply heat to the valve cavity, the target medium in the valve cavity can be kept in a low-viscosity state, the risk of condensation, adhesion or stickiness of the target medium in the valve cavity, valve disc and air passage area can be reduced, and the opening and closing reliability and air passage stability of the breathing valve can be improved.

Description

Technical Field

[0001] This invention relates to the field of breather valve insulation technology, and in particular to a breather valve with an insulation jacket and a method for determining the target flow thickness. Background Technology

[0002] Breather valves are typically installed on storage tanks, containers, or pipeline systems to release or draw air when the internal pressure of the equipment increases or decreases, thereby maintaining the internal pressure within a safe range. For equipment storing or transporting high-viscosity or easily condensable media such as heavy oil, residual oil, sludge oil, and asphalt, media vapors, entrained droplets, or condensate residues can easily condense, adhere, or stick in the valve cavity, valve disc, valve seat, airflow passage, and ventilation area of ​​the breather valve. This leads to increased valve disc opening resistance and unstable reseating, thus affecting the reliability of the breather valve's opening and closing and the stability of its ventilation.

[0003] Existing breather valves typically employ passive insulation structures such as vacuum layers, insulation cotton, insulation layers, or external heat shields. These structures primarily reduce heat loss between the valve body and the external environment, but they cannot continuously replenish heat to the valve cavity. When the external ambient temperature is low, or when the target medium itself has a high viscosity and high freezing point, passive insulation alone is insufficient to maintain the valve cavity within the temperature range required for the target medium to reach a low viscosity state over a long period. Low-temperature cold zones may still form in the valve cavity, valve disc, airflow channels, and ventilation areas. Summary of the Invention

[0004] 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.

[0005] One object of the present invention is to provide a breather valve with an insulating jacket.

[0006] To achieve the above objectives, the present invention adopts the following technical solution: a breather valve with a heat-insulating jacket, comprising a valve body having a valve cavity formed therein; a heat-insulating jacket, disposed on the outside of the valve body, forming a heating medium flow cavity between the jacket and the valve body; the heating medium flow cavity extends along the outer wall of the valve body, and the heating medium flow cavity has a consistent target flow thickness D in its extending direction; among multiple candidate flow thicknesses d i In this context, the target flow thickness D is the minimum candidate flow thickness that satisfies the low viscosity heat preservation condition; the low viscosity heat preservation condition satisfies: , The target flow thickness D satisfies: , Where, d iFor the i-th candidate flow thickness among multiple candidate flow thicknesses, T h To preset the heating medium temperature, T i (d) i T h ( ) is at the preset heating medium temperature T h Below, the heating medium is introduced with the i-th candidate flow thickness d. i The temperature T of the valve chamber after the heating medium flows through the flow chamber. ref The reference temperature of the target medium is ν0, where ν0 is the target medium at the reference temperature T. ref The kinematic viscosity at the following value, ν g The preset kinematic viscosity threshold is the threshold value corresponding to the target medium being in a preset low viscosity state, and k is the viscosity-temperature coefficient of the target medium.

[0007] As a preferred embodiment of the breather valve with a heat-insulating jacket according to the present invention, the valve cavity has multiple heat-insulating evaluation areas, including a positive pressure valve disc area, a negative pressure valve disc area, a valve cavity wall area, and an airflow channel area communicating with the valve cavity; the temperature T i (d) i T h ) is the temperature of the preset heating medium T h Below, the lowest temperature in the multiple insulation evaluation areas.

[0008] As a preferred embodiment of the breather valve with heat-insulating jacket of the present invention, the valve body is provided with an airflow channel communicating with the valve cavity, an airflow channel heating sleeve is provided on the outer periphery of the airflow channel, a channel heating cavity is formed between the airflow channel heating sleeve and the valve body, and the channel heating cavity is communicating with the heating medium flow cavity.

[0009] As a preferred embodiment of the breather valve with heat insulation jacket described in this invention, the valve body is provided with a valve cover at the top. The valve cover includes a valve cover body and an arc-shaped cover. The valve cover body is placed on the top of the valve body, and the arc-shaped cover is located on the side of the valve cover body away from the valve cavity. A valve cover heating cavity is formed between the arc-shaped cover and the valve cover body.

[0010] As a preferred embodiment of the breather valve with heat insulation jacket described in this invention, the valve cover is provided with a negative pressure valve core, the negative pressure valve core includes a valve cover located in the valve cavity and a valve rod connected to the valve cover, the valve rod passes through the valve cover body and extends into the valve cover heating cavity; the valve cover heating cavity is in communication with the heating medium flow cavity.

[0011] As a preferred embodiment of the breather valve with heat-insulating jacket of the present invention, wherein: the arc-shaped cover is provided with a first flow pipe communicating with the heating chamber of the valve cover, the heat-insulating jacket is provided with a second flow pipe communicating with the heating medium flow chamber, the first flow pipe and the second flow pipe are spaced apart along the height direction of the valve body, and the first flow pipe is located above the second flow pipe.

[0012] In a preferred embodiment of the breather valve with a heat-insulating jacket according to the present invention, the valve cover heating chamber and the heating medium flow chamber are connected by a detachable communication component. The detachable communication component includes a first communication pipe disposed on the arc-shaped cover and connected to the valve cover heating chamber, and a second communication pipe disposed on the heat-insulating jacket and connected to the heating medium flow chamber. The connection ends of the first communication pipe and the second communication pipe are arranged opposite to each other along the disassembly direction of the valve cover relative to the valve body.

[0013] As a preferred embodiment of the breather valve with heat-insulating jacket described in this invention, wherein: the first flow pipe has a first extension section extending into the valve cover heating cavity, the first connecting pipe has a second extension section extending into the valve cover heating cavity, the length of the first extension section extending into the valve cover heating cavity along the height direction of the valve body is L1, the length of the second extension section extending into the valve cover heating cavity along the height direction of the valve body is L2, and L2 > L1.

[0014] In a preferred embodiment of the breather valve with heat-insulating jacket described in this invention, the projection range of the valve cover heating cavity on the valve cover body along the height direction of the valve body covers the projection range of the valve cavity on the valve cover body along the height direction of the valve body.

[0015] Another object of the present invention is to provide a method for determining the target flow thickness of a breather valve with an insulating jacket.

[0016] This invention employs the following technical solution: a method for determining the target flow thickness of a breather valve with a thermal insulation jacket, comprising: acquiring the viscosity-temperature reference parameters of the target medium and a preset kinematic viscosity threshold ν. g and the preset heating medium temperature T h The viscosity-temperature reference parameter includes a reference temperature T. ref The target medium at the reference temperature T ref The kinematic viscosity ν0 and the viscosity-temperature coefficient k of the target medium are determined; the preset heating medium temperature T is determined. h And set multiple candidate flow thicknesses d i For each of the candidate flow thicknesses d i At the preset heating medium temperature Th Next, the heating medium is introduced into the channel with the corresponding candidate flow thickness d. i The heating medium flows through the valve chamber, and the temperature T corresponding to the valve chamber is obtained. i (d) i T h ); determine the candidate flow thickness d i Does it meet the low viscosity insulation condition? The low viscosity insulation condition is satisfied as follows: , The candidate flow thickness d that satisfies the low viscosity heat preservation condition i In the middle, the candidate flow thickness d with the smallest value is selected. i The target flow thickness D is determined, and the target flow thickness D satisfies: , Among them, d is involved in determining the target flow thickness D. i Candidate flow thickness to meet the low viscosity insulation conditions.

[0017] In a preferred embodiment of the method for determining the target flow thickness of a breather valve with a thermal insulation jacket as described in this invention, the temperature T corresponding to the valve cavity is obtained. i (d) i T h When ), with the corresponding candidate flow thickness d i Multiple temperature detection points are set on the breathing valve prototype. These multiple temperature detection points include a first temperature detection point located in the positive pressure valve disc area, a second temperature detection point located in the negative pressure valve disc area, a third temperature detection point located in the valve cavity wall area, and a fourth temperature detection point located in the airflow channel area. The temperature T1 of the positive pressure valve disc area is obtained through the first temperature detection point, the temperature T2 of the negative pressure valve disc area is obtained through the second temperature detection point, the valve cavity wall temperature T3 is obtained through the third temperature detection point, and the airflow channel area temperature T4 is obtained through the fourth temperature detection point. The lowest temperature among the positive pressure valve disc area temperature T1, the negative pressure valve disc area temperature T2, the valve cavity wall temperature T3, and the airflow channel area temperature T4 is determined as the candidate flow thickness d. i At the preset heating medium temperature T h The corresponding temperature T i (d) i T h ).

[0018] The beneficial effects of this invention are as follows: By setting an insulation jacket on the outside of the valve body and forming a heating medium flow cavity extending along the outer wall of the valve body between the insulation jacket and the valve body, the heating medium can form a continuous active flow heat exchange path on the outside of the valve body, thereby continuously replenishing heat to the valve body and valve cavity. Compared with passive insulation structures such as insulation cotton, vacuum layer or heat insulation cover, this invention can improve the temperature maintenance capability of the valve cavity, valve disc and ventilation area, reduce the risk of condensation, adhesion or sticking of the target medium inside the breather valve, and improve the opening and closing reliability and ventilation stability of the breather valve.

[0019] This invention incorporates the kinematic viscosity of the target medium at a reference temperature, a preset kinematic viscosity threshold, and the viscosity-temperature coefficient into low-viscosity insulation conditions. This allows the physical properties of the target medium to be transformed into valve cavity temperature compliance requirements, thus providing a clear basis for determining the target flow thickness D based on the medium's physical properties. This avoids insufficient heat compensation due to setting the insulation temperature solely based on experience, and also prevents excessive increases in the flow thickness from leading to larger insulation jacket dimensions, increased heating medium usage, and higher manufacturing costs. Attached Figure Description

[0020] 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.

[0021] Figure 1 This is a schematic diagram of the heating medium flow cavity and target flow thickness of the present invention.

[0022] Figure 2 This is a schematic diagram of the airflow channel, airflow channel heating sleeve, and channel heating cavity structure of the present invention.

[0023] Figure 3 This is a schematic diagram of the structure of the airflow channel heating sleeve and valve body of the present invention.

[0024] Figure 4 This is a cross-sectional structural diagram of the valve cover heating chamber, negative pressure valve core, and detachable connecting assembly of the present invention.

[0025] Figure 5 For the present invention Figure 4 A magnified view of a portion of point A in the middle.

[0026] Figure 6 This is a schematic diagram of the structure of the first flow tube, the second flow tube, and the detachable communication component of the present invention.

[0027] Figure 7 This is a schematic diagram of the structure of the first and second extension pipe sections of the present invention.

[0028] Figure 8 This is a schematic diagram showing the arrangement of temperature detection points in the breather valve with thermal insulation jacket of the present invention.

[0029] Figure 9 This is a temperature change curve of the breather valve with heat insulation jacket of the present invention under the condition of heating medium at 80°C, corresponding to different candidate flow thicknesses in each temperature measurement area.

[0030] Figure 10 This is a graph showing the temperature rise trend of the breather valve with insulation jacket of the present invention under 80°C heating medium conditions in each temperature measurement zone.

[0031] Figure 11 This is a graph showing the temperature rise trend of the breather valve with insulation jacket of the present invention under a heating medium at 150°C in each temperature measurement zone.

[0032] In the diagram: 100, valve body; 101, valve cavity; 102, airflow channel; 200, insulation jacket; 201, heating medium flow cavity; 202, second flow pipe; 300, airflow channel heating sleeve; 301, channel heating cavity; 400, valve cover; 401, valve cover body; 402, arc-shaped cover; 403, valve cover heating cavity; 404, first flow pipe; 404a, first extension pipe section; 500, negative pressure valve core; 501, valve cover; 502, valve stem; 600, detachable connecting assembly; 601, first connecting pipe; 601a, second extension pipe section; 602, second connecting pipe; D, target flow thickness. Detailed Implementation

[0033] 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.

[0034] 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.

[0035] Example 1

[0036] Reference Figure 1This embodiment provides a breather valve with an insulating jacket, comprising a valve body 100 and an insulating jacket 200. A valve cavity 101 is formed within the valve body 100, serving as a gas flow space, a valve disc opening and closing space, and a medium vapor passage space for the breather valve. The insulating jacket 200 is located outside the valve body 100, forming a heating medium flow cavity 201 between it and the valve body 100. The heating medium flow cavity 201 is used to supply hot water, steam, heat transfer oil, or other heating media, enabling the heating media to form an active heat exchange path along the outer wall of the valve body 100.

[0037] The heating medium flow cavity 201 extends along the outer wall of the valve body 100 and has a consistent target flow thickness D in its extension direction. This consistency does not require the valve body 100 to be a regular cylinder, nor does it require every local manufacturing error to be exactly the same. Rather, it means that the effective flow spacing of the heating medium flow cavity 201 along the main heat exchange path is designed according to the same target thickness, so that when the heating medium flows along the outer periphery of the valve body 100, there will be no section that is too narrow, resulting in a significant increase in flow resistance, nor will there be any section that is too wide, resulting in local volume redundancy.

[0038] The target flow thickness D is not an arbitrary interlayer distance determined based on processing experience in a typical jacket, but rather is determined by multiple candidate flow thicknesses d. i The structural parameters obtained through screening. Specifically, multiple candidate flow thicknesses d can be preset. i Examples include 3mm, 5mm, 7mm, 9mm, 11mm, 13mm, 15mm, 17mm, 19mm, 21mm, 23mm, and 25mm. Each candidate flow thickness d i Each corresponds to a fabricable or simulateable heating medium flow cavity 201, and corresponds to a preset heating medium temperature T. h The valve chamber temperature T formed below i (d) i T h ).

[0039] Low viscosity insulation conditions can be expressed as: , Among them, T ref ν0 is the reference temperature of the target medium at the reference temperature T. ref The kinematic viscosity at the following value, ν g The preset kinematic viscosity threshold corresponds to the target medium being in a preset low viscosity state, where k is the viscosity-temperature coefficient of the target medium. Reference temperature T ref This is not the temperature of the heating medium, but rather the reference temperature for the viscosity data of the target medium. For example, if the kinematic viscosity of the target medium at 40°C is measured to be ν0, then 40°C can be used as T. ref ν0 is the kinematic viscosity at this reference temperature.

[0040] The right side of the above inequality represents the decrease in the target medium's viscosity from the reference viscosity to the preset kinematic viscosity threshold ν. g Required temperature. (Left side T) i (d) i T h () indicates that the preset heating medium temperature T h Below, with candidate flow thickness d i After the heating medium flow chamber 201 reheats the valve body 100, the valve chamber 101 reaches the evaluation temperature. Thus, the low viscosity heat preservation condition establishes a correlation between the physical properties of the target medium and the structural thickness of the outer jacket of the valve body, rather than relying solely on empirical temperature or ambient temperature as the basis for judgment.

[0041] In multiple candidate flow thicknesses d i In this process, only candidate thicknesses that meet the above-mentioned low-viscosity insulation conditions are included in the determination of the target flow thickness D. The target flow thickness D satisfies: , Among them, d participates in taking the minimum value i The candidate flow thickness already meets the low viscosity insulation requirements. In this embodiment, instead of directly selecting the minimum value from all candidate thicknesses, it first filters out candidate thicknesses that cannot meet the low viscosity insulation requirements of valve cavity 101 based on the target medium viscosity requirement. Then, it selects the minimum value as D from the remaining compliant candidate thicknesses. This method avoids the existence of a low-temperature region in the valve cavity due to an excessively small jacket, and also avoids increasing the size of the insulation jacket 200, the volume of the heating medium, and manufacturing costs due to simply pursuing a larger flow space.

[0042] Example 2

[0043] Reference Figure 1 and Figure 8 This embodiment provides a temperature T i (d) i T h The evaluation method is as follows: The valve cavity 101 has multiple insulation evaluation areas, including the positive pressure valve disc area, the negative pressure valve disc area, the valve cavity wall area, and the airflow channel area connected to the valve cavity 101.

[0044] The positive pressure valve disc area reflects the insulation status of the positive pressure exhaust part of the breather valve. If the temperature in this area is too low, target medium vapor, entrained droplets, or condensed residues are likely to adhere to the positive pressure valve disc or the corresponding valve seat, thereby increasing the opening resistance of the positive pressure valve disc or affecting the reseating stability. The negative pressure valve disc area reflects the insulation status of the negative pressure intake part of the breather valve. If the temperature in this area is too low, the target medium is likely to form viscosity near the negative pressure valve core 500, valve cover 501, or valve stem 502, thereby affecting the sensitivity of the negative pressure valve core 500. The valve cavity wall area reflects the insulation status of the heat exchange area of ​​the valve body 100. Its temperature reflects the heat replenishment effect of the heating medium flow cavity 201 on the side wall of the valve body 100. The airflow channel area reflects the insulation status of the connection between the valve cavity 101 and the external ventilation area. Because the airflow channel area is close to the external environment or external pipelines, the heat dissipation path is short, and it is usually easier to form a relatively low temperature area.

[0045] In determining the candidate flow thickness d i The corresponding temperature T i (d) i T h When evaluating insulation, the temperature of a single valve cavity wall is not used as the evaluation temperature, nor is the average temperature of multiple insulation evaluation areas used as the evaluation temperature. Instead, the lowest temperature among the multiple insulation evaluation areas is determined as T. i (d) i T h For example, at a preset heating medium temperature T h Below, the i-th candidate flow thickness d i After the heating medium is introduced into the heating medium flow chamber 201 and a stable heat exchange state is reached, the temperatures of the positive pressure valve disc region, the negative pressure valve disc region, the valve chamber wall region, and the airflow channel region are obtained respectively, and the lowest value among the above temperatures is taken as T. i (d) i T h ).

[0046] Use the lowest temperature as T i (d) i T h The reason is that the reliability of the breather valve's opening and closing depends not only on whether the main body area of ​​the valve chamber 101 meets the insulation requirements, but also on whether there are still low-temperature limiting areas in the positive pressure valve disc area, negative pressure valve disc area, valve chamber wall area, and airflow channel area. If the temperature of any of these areas is lower than the temperature required for the target medium to reach the preset low viscosity state, the target medium may still condense, adhere, or stick in that area, thus affecting the overall reliability of the breather valve's operation.

[0047] Therefore, the lowest temperature in multiple insulation evaluation areas is taken as T. i (d)i T h This allows the determination of the target flow thickness D to cover the low-temperature risk locations inside the breathing valve and in the ventilation connection area. Therefore, in judging candidate flow thicknesses d... i When the low viscosity insulation condition is met, the higher temperature in the positive pressure valve disc area, negative pressure valve disc area, or valve cavity wall area will not mask the lower temperature in the airflow channel area, nor will the use of average temperature weaken the local low temperature area. This evaluation method can improve the reliability of determining the target flow thickness D, making the selected target flow thickness D more suitable for ensuring the opening and closing stability and ventilation stability of the breather valve under high viscosity or easily condensable target media conditions.

[0048] Example 3

[0049] Reference Figure 2 and Figure 3 The valve body 100 is provided with an airflow passage 102 communicating with the valve chamber 101. The airflow passage 102 can be an exhaust passage, an intake passage, a flame arrestor passage, or a lateral passage connected to a flame arrestor assembly. Since the airflow passage 102 is usually close to the external environment or external pipelines, its metal wall, flame arrestor plate, or ventilation components are prone to forming a relatively low temperature area, which is a high-risk location for the adhesion and sticking of target medium vapor, entrained droplets, or condensed droplets.

[0050] To prevent the airflow channel 102 from becoming a break in the active insulation path, an airflow channel heating sleeve 300 is provided around the outer periphery of the airflow channel 102. The airflow channel heating sleeve 300 can be fitted onto the outside of the airflow channel 102, or it can form a partial covering structure together with the outer wall of the valve body 100. A channel heating cavity 301 is formed between the airflow channel heating sleeve 300 and the valve body 100. The channel heating cavity 301 is connected to the heating medium flow cavity 201, allowing the heating medium to continue flowing from the main peripheral area of ​​the valve body 100 into the outer periphery of the airflow channel 102.

[0051] The function of the channel heating chamber 301 is not only to expand the heat exchange area, but more importantly, to incorporate the airflow channel 102 into the overall insulation system corresponding to the target flow thickness D. If the heating medium flow chamber 201 is only set on the outer periphery of the valve body 100, and the outer periphery of the airflow channel 102 is not covered by the heating medium, even if the main body area of ​​the valve cavity 101 reaches the low viscosity insulation condition, the area near the airflow channel 102 may still form a minimum temperature point due to strong heat dissipation. This minimum temperature point will cause the target medium to condense at the airflow channel 102 or the flame arrestor, and may cause the channel cross-section to shrink, the valve disc to become unstable when reseating, or the flame arrestor channel to become blocked.

[0052] Example 4

[0053] Reference Figure 4 and Figure 5A valve cover 400 is provided on the top of the valve body 100. The valve cover 400 includes a valve cover body 401 and an arc-shaped cover 402. The valve cover body 401 covers the top of the valve body 100, and is used to close the top opening of the valve cavity 101 and provide a mounting base for the valve core component. The arc-shaped cover 402 is located on the side of the valve cover body 401 opposite to the valve cavity 101, and forms a valve cover heating cavity 403 between the cover body 402 and the valve cover body 401.

[0054] The valve cover heating chamber 403 is used to actively heat the valve cover body 401 and the top area of ​​the valve cavity 101. The top area of ​​the breather valve usually has a large exposed area and is in full contact with the outside air, making it easy to form a path for heat dissipation from the valve cover body 401 outward. If the heating medium only flows along the side wall of the valve body 100, and there is no heating space above the valve cover body 401, the top area of ​​the valve cavity 101 may still be lower than the temperature of the side wall area, forming a cold spot that affects the operation of the negative pressure valve core.

[0055] The arc-shaped cover 402 preferably forms a cover structure that protrudes away from the valve cover body 401, so that the valve cover heating chamber 403 has a stable medium-containing space above the valve cover body 401. This cover structure can be installed on the valve cover body 401 by welding, screwing, flange pressing, or integral molding. The arc surface of the arc-shaped cover 402 helps to reduce dead angles in the cavity, allowing steam, hot water, or heat transfer oil to diffuse in the valve cover heating chamber 403, and enabling heat to be transferred along the valve cover body 401 to the top of the valve cavity 101.

[0056] The valve cover heating chamber 403 extends the heat preservation path of the present invention from the periphery of the valve body 100 to the top of the valve body 100. This top heat replenishment structure, together with the heating medium flow chamber 201, forms a composite heat exchange system of lateral heat replenishment and top heat replenishment, which can improve the problem of traditional jackets only surrounding the side wall of the valve body and neglecting the heat dissipation of the valve cover. Especially when the target medium is asphalt, heavy oil, or residual oil, once a low-temperature cold spot forms in the top valve cover area, condensate will accumulate near the valve stem or valve cover, increasing the opening and closing resistance.

[0057] Example 5

[0058] Reference Figure 4 and Figure 5 This embodiment provides a mating structure between the negative pressure valve core 500 and the valve cover heating chamber 403. The valve cover 400 is provided with the negative pressure valve core 500, which includes a valve cover 501 located within the valve chamber 101 and a valve stem 502 connected to the valve cover 501. The valve stem 502 passes through the valve cover body 401 and extends into the valve cover heating chamber 403.

[0059] The negative pressure valve core 500 is used to open when the pressure inside the tank or container is lower than the external pressure, allowing external gas to enter the equipment. This type of valve core typically has a small opening pressure differential and high responsiveness. If the target medium condenses, adheres, or sticks in the areas through which it passes in the valve cover 501, valve stem 502, or valve cover body 401, even a small amount of adhesion can significantly increase the opening resistance of the negative pressure valve core 500 or affect its reseating stability.

[0060] In this embodiment, the valve stem 502 extends into the valve cover heating chamber 403, which places the area where the valve stem passes through near the active heating space. The heating medium in the valve cover heating chamber 403 can transfer heat to the valve stem passage location through the valve cover body 401 and the surrounding structure of the valve stem 502, making it less likely for a low-temperature cold spot to form at that location. After the valve cover 501 is connected to the valve stem 502, the thermal state of the valve stem 502 can also affect the temperature around the valve cover 501, thereby reducing the risk of the target medium sticking at the critical moving parts of the negative pressure valve core 500.

[0061] The valve cover heating chamber 403 is connected to the heating medium flow chamber 201, allowing the heating medium to flow not only laterally along the outer wall of the valve body 100 but also to continue flowing into the top area of ​​the valve cover 400. Therefore, the installation area of ​​the negative pressure valve core 500 can be included in the same heating medium circulation path. Compared to separately installing an electric heating belt or local insulation sleeve outside the valve stem, this embodiment does not require an independent heat source at the valve stem insertion point. Instead, it utilizes the connection between the heating medium flow chamber 201 and the valve cover heating chamber 403 to achieve unified heat replenishment, resulting in a more compact structure and fewer maintenance points.

[0062] Example 6

[0063] Reference Figure 4 , Figure 5 and Figure 6 This embodiment provides a high-low arrangement of the heating medium inlet and outlet pipelines. The arc-shaped cover 402 is provided with a first flow pipe 404 communicating with the valve cover heating chamber 403, and the insulation jacket 200 is provided with a second flow pipe 202 communicating with the heating medium flow chamber 201. The first flow pipe 404 and the second flow pipe 202 are spaced apart along the height direction of the valve body 100, and the first flow pipe 404 is located above the second flow pipe 202.

[0064] The first flow pipe 404 can serve as either an inlet or an outlet for the heating medium; similarly, the second flow pipe 202 can also serve as either an inlet or outlet depending on the phase of the heating medium and the on-site piping conditions. The key is that the two are staggered along the height direction, allowing the heating medium to form a vertical flow path across the valve cover heating chamber 403 and the heating medium flow chamber 201, rather than simply circulating a short distance within a local chamber.

[0065] When the heating medium is a liquid medium such as hot water or heat transfer oil, a bottom-in, top-out configuration is preferred, with the second flow pipe 202 inlet and the first flow pipe 404 outlet. The liquid heating medium enters the heating medium flow chamber 201 from a lower position, gradually fills the space around the valve body 100 and the valve cover heating chamber 403, and finally exits through the first flow pipe 404 at a higher position. This flow method facilitates the removal of air from the chamber, reduces air resistance and local cavities, and ensures a better degree of filling of the chamber with the liquid heating medium.

[0066] When the heating medium is a gaseous medium such as steam, a top-in, bottom-out configuration can be adopted, with the first flow pipe 404 inlet and the second flow pipe 202 outlet. After entering the valve cover heating chamber 403 from the top, the steam first reheats the valve cover body 401, the area through which the valve stem 502 passes, and the top of the valve chamber, before flowing along the connecting path to the heating medium flow chamber 201 and the channel heating chamber 301. The condensate formed by steam condensation can be discharged through the lower-positioned second flow pipe 202, reducing the risk of condensate retention leading to a decrease in heat exchange efficiency.

[0067] Example 7

[0068] Reference Figure 4 , Figure 5 and Figure 6 This embodiment provides a detachable communication assembly 600 between the valve cover heating chamber 403 and the heating medium flow chamber 201. The detachable communication assembly 600 includes a first communication pipe 601 and a second communication pipe 602. The first communication pipe 601 is disposed in the arc-shaped cover 402 and communicates with the valve cover heating chamber 403; the second communication pipe 602 is disposed in the heat insulation jacket 200 and communicates with the heating medium flow chamber 201.

[0069] The connecting ends of the first connecting pipe 601 and the second connecting pipe 602 are positioned opposite each other along the disassembly direction of the valve cover 400 relative to the valve body 100. This relative arrangement allows the valve cover 400 to be moved away along the disassembly direction after the sealing connection between the first connecting pipe 601 and the second connecting pipe 602 needs to be released when the negative pressure valve core 500, valve cover 501, valve stem 502, or valve seat area needs to be inspected, without the valve cover 400 being obstructed due to the interlaced arrangement of the connecting pipes.

[0070] The connection between the first connecting pipe 601 and the second connecting pipe 602 can be formed into a detachable sealed connection through flanges, quick-release clamps, threaded joints, or compression fittings with gaskets. Preferably, when a flange connection is used, the end faces of the two flanges face each other along the disassembly direction of the valve cover 400. Removing the fasteners will disconnect the connection between the valve cover heating chamber 403 and the heating medium flow chamber 201. A gasket can be placed between the two flange end faces to prevent leakage of hot water, heat transfer oil, steam, or condensate.

[0071] In this embodiment, a detachable connection structure is formed by the first connecting pipe 601 and the second connecting pipe 602, which ensures that an active heat exchange channel is formed between the valve cover heating chamber 403 and the heating medium flow chamber 201, while retaining the ability to disassemble and maintain the valve cover 400.

[0072] Example 8

[0073] Reference Figure 7 This embodiment provides a staggered flow path structure within the valve cover heating cavity 403. The first flow pipe 404 has a first extension section 404a extending into the valve cover heating cavity 403, and the first connecting pipe 601 has a second extension section 601a extending into the valve cover heating cavity 403. The length of the first extension section 404a extending into the valve cover heating cavity 403 along the height direction of the valve body 100 is L1, and the length of the second extension section 601a extending into the valve cover heating cavity 403 along the height direction of the valve body 100 is L2, where L2 is greater than L1.

[0074] Since L2 is greater than L1, the opening positions of the first extension pipe section 404a and the second extension pipe section 601a in the valve cover heating chamber 403 are staggered along the height direction. This staggering is not simply a change in pipe length, but rather to prevent the heating medium from forming a short-circuit flow directly between the two openings. If the heights of the two openings are close, the heating medium entering the valve cover heating chamber 403 may exit directly from the other opening along the shortest path, resulting in insufficient heat exchange in the upper or edge areas of the valve cover heating chamber 403.

[0075] When the heating medium is hot water or heat transfer oil, and the second flow pipe 202 is used for inlet and the first flow pipe 404 is used for outlet, the heating medium enters a deeper position in the valve cover heating chamber 403 through the second connecting pipe 602, the first connecting pipe 601, and the second extension pipe section 601a. ​​It then diffuses upwards or circumferentially within the chamber, and subsequently exits through the shallower first extension pipe section 404a into the first flow pipe 404. This flow path can improve the flushing and filling effect of the liquid heating medium on the bottom and middle areas of the valve cover heating chamber 403.

[0076] When the heating medium is steam, and the first flow pipe 404 is used for inlet and the second flow pipe 202 is used for outlet, the steam first enters the valve cover heating chamber 403 near the upper part through the shallower first insertion pipe section 404a. After diffusing and releasing heat in the chamber, it is then led out through the deeper second insertion pipe section 601a to the first connecting pipe 601 and the heating medium flow chamber 201. The diffusion time and heat exchange path of the steam in the chamber are extended, and the condensate is more easily discharged along the lower path.

[0077] The technical advantage of this embodiment is that it reduces the risk of short-circuit flow and local stagnation in the valve cover heating chamber 403, allowing the heating medium to form a more complete flow coverage in the valve cover heating chamber 403. As a result, the valve cover body 401, the area through which the valve stem 502 passes, and the top area of ​​the valve cavity 101 can obtain more uniform heat replenishment.

[0078] Example 9

[0079] Reference Figure 4 and Figure 5 This embodiment provides a top covering structure for the valve cover heating cavity 403. The projection range of the valve cover heating cavity 403 on the valve cover body 401 along the height direction of the valve body 100 covers the projection range of the valve cavity 101 on the valve cover body 401 along the height direction of the valve body 100.

[0080] The projection range coverage here refers to the heating coverage area formed by the valve cover heating cavity 403 on the valve cover body 401 when viewed from the height direction of the valve body 100. This area is not smaller than the corresponding area of ​​the valve cavity 101 on the valve cover body 401. The valve cover heating cavity 403 is not just a small local cavity around the valve stem 502, nor is it just a narrow flow channel formed at the edge of the valve cover body 401. Instead, it can cover the main heat dissipation area at the top of the valve cavity 101.

[0081] The top region of valve cavity 101 has a significant impact on the opening and closing reliability of the breather valve. On the one hand, the negative pressure valve core 500 is usually located near the valve cover 400, with its valve stem 502 passing through the valve cover body 401, and the valve cover 501 located at the top of valve cavity 101. On the other hand, the valve cover body 401 has a large contact area with the outside, making it a path for heat dissipation from valve cavity 101. If the coverage area of ​​the valve cover heating chamber 403 is insufficient, the edge of the top of valve cavity 101 or the area far from the valve stem may still be lower than the low viscosity insulation temperature of the target medium.

[0082] By ensuring that the projected area of ​​the valve cover heating cavity 403 covers the projected area of ​​the valve cavity 101, the heating medium can provide overall supplementary heating to the area in the valve cover body 401 corresponding to the top of the valve cavity 101, allowing heat to enter the valve cavity 101 from the top direction. This top supplementary heating, combined with the lateral supplementary heating of the heating medium flow cavity 201 along the outer wall of the valve body, forms a synergistic lateral and top heat preservation system.

[0083] Example 10

[0084] Reference Figure 8 This embodiment provides a method for determining the target flow thickness of a breather valve with an insulation jacket. This method is used to determine the target flow thickness D of the heating medium flow cavity 201 between the insulation jacket 200 and the valve body 100 during the breather valve structural design stage, ensuring that the structural dimensions simultaneously meet the requirements for low-viscosity insulation and to prevent jacket redundancy.

[0085] First, obtain the viscosity-temperature reference parameters of the target medium and the preset kinematic viscosity threshold ν. g and the preset heating medium temperature T h Viscosity-temperature reference parameters include the reference temperature T. ref The target medium at the reference temperature T ref The kinematic viscosity ν0 and the viscosity-temperature coefficient k of the target medium. Reference temperature T. ref It can come from the target medium test report, physical property data sheet or on-site sampling test results; ν0 is the kinematic viscosity of the target medium at this reference temperature; k is used to characterize the rate at which the kinematic viscosity of the target medium decreases with increasing temperature.

[0086] The viscosity-temperature coefficient k can be obtained by fitting multiple sets of viscosity test data of the target medium. For example, if the target medium is at temperature T... a The kinematic viscosity at the following value is ν a At temperature T b The kinematic viscosity at the following value is ν b Then, k can be determined based on the approximately linear relationship between lnν and temperature, allowing the viscosity-temperature relationship of the target medium to be used to deduce the temperature requirements corresponding to the low viscosity state. A preset kinematic viscosity threshold ν is used. g The viscosity can be determined based on the maximum viscosity allowed for normal opening and closing of the breather valve, for example, by using the criterion that the target medium does not easily form obvious viscosity in the valve disc, valve seat, or airflow channel.

[0087] Then, multiple candidate flow thicknesses d are set. i Candidate flow thickness d i The thickness range should be covered, from significantly too small to potentially too large, to allow for observation of the valve cavity temperature variation with flow thickness. For example, for a DN150 sample, multiple candidate values ​​between 3 mm and 25 mm can be set. Each candidate flow thickness d i Each corresponds to a breathing valve prototype, a simulation model, or an adjustable test chamber.

[0088] For each candidate flow thickness d i At the preset heating medium temperature T h Next, the heating medium is introduced into the channel with the corresponding candidate flow thickness d. i The heating medium flows through the chamber 201, and the temperature T corresponding to the valve chamber 101 is obtained. i (d) i T h ). Here, T i (d) i T hThe evaluation temperature should be obtained under the same testing rules, such as after reaching a steady state or after a preset heating time. The heating medium type, inlet temperature, flow rate, ambient temperature, and testing time should be kept consistent between different candidate flow thicknesses to ensure that the comparison results reflect the influence of the flow thickness itself on the heat compensation effect.

[0089] Then determine the candidate flow thickness d. i Does it meet the low viscosity insulation requirements? , If a certain candidate flow thickness d i The corresponding T i (d) i T h If the temperature is lower than the temperature requirement calculated from the target medium viscosity-temperature parameters on the right, it indicates that the heating medium flow chamber 201 at this candidate flow thickness cannot bring the valve chamber 101 to the temperature required for the target medium to reach a low viscosity state. Therefore, this candidate flow thickness is not included in the value of the target flow thickness D. If a certain candidate flow thickness d... i The corresponding T i (d) i T h If the temperature is not lower than the required temperature, it means that the candidate thickness can meet the low viscosity insulation conditions.

[0090] Finally, the candidate flow thickness d that meets the low viscosity insulation requirements. i In the middle, the candidate flow thickness d with the smallest value is selected. i The target flow thickness is determined to be D, i.e.: , The key to this value selection logic is "meeting the standard first, then minimizing." When the candidate thickness is small, the heating medium flow cross-section is insufficient, resulting in inadequate heat exchange capacity, and a low-temperature region is easily formed near the valve cavity 101 or airflow channel 102. When the candidate thickness is large, the valve cavity temperature may continue to increase, but the volume, materials, heating medium volume, and manufacturing cost of the insulation jacket 200 will also increase. By determining the minimum thickness that meets the low-viscosity insulation conditions as D, a clear technical balance can be established between insulation reliability and structural economy.

[0091] Example 11

[0092] Reference Figures 8 to 11 This embodiment provides a method for obtaining the temperature T corresponding to valve chamber 101. i (d) i T h The specific method of determining the target flow thickness D is explained, along with experimental data. T is obtained. i (d) i T hWhen ), with the corresponding candidate flow thickness d i Multiple temperature detection points are set on the breathing valve prototype. These multiple temperature detection points include a first temperature detection point located in the positive pressure valve disc area, a second temperature detection point located in the negative pressure valve disc area, a third temperature detection point located in the valve cavity wall area, and a fourth temperature detection point located in the airflow channel area.

[0093] The temperature T1 of the positive pressure valve disc area is obtained through the first temperature detection point, the temperature T2 of the negative pressure valve disc area is obtained through the second temperature detection point, the temperature T3 of the valve cavity wall is obtained through the third temperature detection point, and the temperature T4 of the airflow channel area is obtained through the fourth temperature detection point. The above four areas represent the exhaust opening and closing part of the breathing valve, the inhalation opening and closing part, the heat exchange part of the valve cavity body, and the part near the airflow channel that is prone to heat loss, respectively.

[0094] This embodiment does not directly use the average of the four temperatures as T. i (d) i T h Instead, the lowest temperature among T1, T2, T3, and T4 is determined as T. i (d) i T h If any of the four critical zones remains below the low-viscosity insulation condition, the target medium may condense, adhere, or become sticky in that zone, thus affecting the overall operation of the breather valve. Therefore, using the lowest temperature as the evaluation temperature is more rigorous and reliable than using the average temperature or a single wall surface temperature as the evaluation criterion.

[0095] Taking a DN150 jacketed breather valve sample as an example, the temperature measurement results corresponding to different candidate flow thicknesses under 80℃ heating medium conditions are shown in the table below. This data is used to illustrate the temperature changes in the positive pressure valve disc area, negative pressure valve disc area, valve cavity wall area, and airflow channel area after the candidate flow thickness is increased.

[0096] Table 1: Temperature data of the measurement area corresponding to different candidate flow thicknesses

[0097] The data in the table shows that when the candidate flow thickness increases from 3mm to 15mm, T1, T2, T3, and T4 all increase significantly, but T4 remains the lowest temperature. This indicates that the airflow channel area or the area near the airflow channel is more prone to low-temperature limitation than the valve body area. At a candidate flow thickness of 15mm, the lowest temperature is 49.5℃. If the target temperature corresponding to the low viscosity insulation condition of the target medium is 53℃, then this thickness still does not meet the requirements.

[0098] When the candidate flow thickness is 17 mm, the minimum temperature reaches 53.0℃, which meets the low viscosity insulation requirements and can be considered the minimum acceptable threshold. Further increasing the thickness to 19 mm and 21 mm results in minimum temperatures of 53.1℃ and 53.3℃ respectively, with only a slight temperature increase. Further increasing to 23 mm and 25 mm results in minimum temperatures of 53.9℃ and 54.2℃ respectively, with a slower temperature increase, but further increases in structural dimensions, jacket volume, and heating medium usage. Therefore, 17 mm can be considered the minimum acceptable thickness, or 19 mm to 21 mm can be considered the preferred range when a safety margin is required.

[0099] To verify the effect of heating medium temperature changes on the temperature rise of valve cavity 101, after determining the target flow thickness D, temperature rise tests can be performed on the same component under heating medium conditions of 80℃ and 150℃. The temperature rise data under the 80℃ condition are shown in the table below.

[0100] Table 2: Temperature rise data for each measurement zone under 80℃ heating medium conditions

[0101] At 80℃, T1, T2, and T3 gradually approached and stabilized at around 66℃ in the later stages, indicating that the positive pressure valve disc area, negative pressure valve disc area, and valve cavity wall area could obtain sufficient heat replenishment. T4 reached 53.1℃ after 4 hours, which was still the lowest temperature among the four measuring points. This shows that the airflow channel area cannot be ignored when evaluating whether the target flow thickness D meets the low viscosity heat preservation conditions.

[0102] The temperature rise data at 150℃ are shown in the table below.

[0103] Table 3: Temperature rise data for each measurement zone under 150℃ heating medium conditions

[0104] At 150℃, the temperature at all measuring points increased significantly overall, indicating that the temperature of the heating medium T h After the improvement, the heating medium flow chamber 201 can further enhance the heat replenishment capacity of the valve body 100, valve chamber 101, and the area near the airflow channel 102. However, T4 is still lower than T1, T2, and T3, indicating that the airflow channel area may still be the lowest temperature area even at higher heating medium temperatures.

[0105] This embodiment also conducted thermal efficiency tests on the super-insulated jacketed breather valve and the ordinary insulated jacketed breather valve. During the tests, the temperature of the heating medium was used as the heat source temperature, and the temperature measurements were as follows: positive pressure valve disc area temperature T1, negative pressure valve disc area temperature T2, valve cavity wall temperature T3, and flame arrestor plate area temperature T4 within the airflow channel. T1, T2, and T3 were used to evaluate the internal heat replenishment effect of the chamber, while T4 was used to evaluate the low-temperature limiting area within the airflow channel region.

[0106] The experimental data of the super-insulated jacketed breathing valve are shown in Table 4 below.

[0107] Table 4: Thermal Efficiency Test Data of Breathing Valve in Super Insulation Jacket

[0108] According to Table 4, under stable operating conditions at 80℃, the average temperatures of T1, T2, and T3 are: (66.2 + 66.9 + 66.3) / 3 = 66.47℃.

[0109] The internal thermal efficiency of the chamber is approximately: 66.47 / 80×100%=83.1%.

[0110] Meanwhile, the temperature T4 in the flame arrestor plate area within the airflow channel is 53.1℃, and its corresponding thermal efficiency is approximately: 53.1 / 80×100%=66.4%.

[0111] Under stable operating conditions at 150℃, the average temperatures of T1, T2, and T3 are: (122.4 + 123.0 + 121.0) / 3 = 122.13℃.

[0112] The internal thermal efficiency of the chamber is approximately: 122.13 / 150×100%=81.4%.

[0113] Meanwhile, the temperature T4 in the flame arrestor plate area within the airflow channel is 90.9℃, and its corresponding thermal efficiency is approximately: 90.9 / 150×100%=60.6%.

[0114] Therefore, it can be seen that the thermal efficiency of the super-insulated jacketed breathing valve under two stable operating conditions of 80℃ and 150℃ is approximately 83.1% and 81.4% respectively, which can be expressed as approximately 82% in total; the thermal efficiency of the flame arrestor plate area in the airflow channel is approximately 66.4% and 60.6% respectively, which can be expressed as approximately 63% in total.

[0115] The experimental data for a standard thermal insulation jacket breather valve are shown in Table 5 below.

[0116] Table 5: Thermal Efficiency Test Data of Breathing Valve in Ordinary Thermal Insulation Jacket

[0117] According to Table 5, under stable operating conditions at 80℃, the average temperatures of T1, T2, and T3 are: (65.2 + 65.5 + 64.6) / 3 = 65.1℃; The internal thermal efficiency of the chamber is approximately: 65.1 / 80×100%=81.4%.

[0118] Meanwhile, the temperature T4 in the flame arrestor plate area within the airflow channel is 51.2℃, and its corresponding thermal efficiency is approximately: 51.2 / 80×100%=64.0%.

[0119] Under stable operating conditions at 150℃, the average temperatures of T1, T2, and T3 are: (119.1 + 121.4 + 118.3) / 3 = 119.6℃.

[0120] The internal thermal efficiency of the chamber is approximately: 119.6 / 150×100%=79.7%.

[0121] Meanwhile, the temperature T4 in the flame arrestor plate area within the airflow channel is 88.6℃, and its corresponding thermal efficiency is approximately: 88.6 / 150×100%=59.1%.

[0122] Therefore, it can be seen that the internal thermal efficiency of a common insulated jacketed breather valve under two stable operating conditions of 80℃ and 150℃ is approximately 81.4% and 79.7% respectively, which can be expressed as approximately 80% in total; the thermal efficiency of the flame arrestor plate area in the airflow channel is approximately 64.0% and 59.1% respectively, which can be expressed as approximately 60% in total.

[0123] It should be noted that the ordinary insulated jacketed breather valve in Table 5 can be understood as a comparative sample. This ordinary insulated jacketed breather valve includes a valve body and an ordinary insulated jacket disposed on the outside of the valve body. An ordinary jacketed flow cavity is formed between the ordinary insulated jacket and the valve body for the flow of the heating medium. This ordinary jacketed flow cavity can provide supplementary heating to the main body area of ​​the valve body, but its coverage and supplementary heating capacity for the top area of ​​the valve cover, the area through which the negative pressure valve core passes, and the area of ​​the flame arrestor plate in the airflow channel is relatively limited. In other words, the ordinary insulated jacketed breather valve mainly relies on the jacketed flow cavity on the outer periphery of the valve body to transfer heat to the main body area of ​​the valve cavity, and does not form a multi-area continuous supplementary heating path as in this embodiment, which is formed by the heating medium flow cavity 201, the channel heating cavity 301, and the valve cover heating cavity 403. Alternatively, the coverage of its supplementary heating path to the airflow channel 102 and the top area of ​​the valve cover 400 is lower than that of the super insulated jacketed breather valve.

[0124] As shown in Tables 4 and 5, under the same or similar heating medium temperature conditions, the overall thermal efficiency of the super-insulated jacketed breather valve is approximately 82% inside the chamber, and approximately 63% in the flame arrestor plate area of ​​the airflow channel; while the overall thermal efficiency of the ordinary insulated jacketed breather valve is approximately 80% inside the chamber, and approximately 60% in the flame arrestor plate area of ​​the airflow channel. This indicates that, compared to the ordinary insulated jacketed breather valve, the super-insulated jacketed breather valve achieves higher thermal efficiency in both the chamber and the flame arrestor plate area of ​​the airflow channel, suggesting that the continuous heat replenishment path formed between the heating medium flow chamber 201, the channel heating chamber 301, and the valve cover heating chamber 403 can improve the overall insulation capability of the breather valve.

[0125] Meanwhile, Tables 4 and 5 also show that, regardless of whether a super-insulated jacketed breather valve or a regular insulated jacketed breather valve is used, the temperature of the flame arrestor plate area in the airflow channel corresponding to T4 is lower than the internal temperature of the chamber corresponding to T1, T2, and T3. Although the super-insulated jacketed breather valve has a better overall insulation effect than the regular insulated jacketed breather valve, the area near the airflow channel 102 is still a relatively low-temperature limiting area. This is because the airflow channel 102 is close to the external ventilation area, has a short heat dissipation path, and its internal flame arrestor plate or ventilation component has a large metal contact area and heat exchange area, making it easy to transfer heat to the external environment or external pipelines. Therefore, the candidate flow thickness d is determined solely by the positive pressure valve plate area temperature T1, the negative pressure valve plate area temperature T2, or the valve chamber wall temperature T3. i Whether the low viscosity insulation conditions are met may mask the fact that the airflow channel area has not yet met the standards.

[0126] Based on the above experimental results, the candidate flow thickness d was determined. i The corresponding temperature T i (d) i T h When evaluating the temperature, the lowest of the following three temperatures is used: positive pressure valve disc temperature T1, negative pressure valve disc temperature T2, valve cavity wall temperature T3, and airflow channel temperature T4. This not only reflects the improved insulation effect of the super-insulated jacketed breather valve compared to the ordinary insulated jacketed breather valve, but also avoids neglecting the low-temperature limiting area of ​​the airflow channel due to focusing only on the temperature of the main valve cavity area. This ensures that the determination of the target flow thickness D takes into account both the overall heat replenishment capacity and the risk of local low temperature, thus improving the reliability of the determination of the target flow thickness D.

[0127] 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 breather valve with an insulated jacket, characterized in that: include, Valve body (100), a valve cavity (101) is formed therein; A heat insulation jacket (200) is provided on the outside of the valve body (100) and forms a heating medium flow cavity (201) between the jacket and the valve body (100). The heating medium flow cavity (201) extends along the outer wall of the valve body (100), and the heating medium flow cavity (201) has a consistent target flow thickness D in its extension direction; In multiple candidate flow thicknesses d i In this context, the target flow thickness D is the minimum candidate flow thickness that satisfies the low viscosity heat preservation condition; The low viscosity heat preservation conditions are satisfied as follows: ， The target flow thickness D satisfies: ， Where, d i For the i-th candidate flow thickness among multiple candidate flow thicknesses, T h To preset the heating medium temperature, T i (d) i T h ( ) is at the preset heating medium temperature T h Below, the heating medium is introduced with the i-th candidate flow thickness d. i The temperature T corresponding to the valve chamber (101) after the heating medium flow chamber (201) is... ref The reference temperature of the target medium is ν0, where ν0 is the target medium at the reference temperature T. ref The kinematic viscosity at the following value, ν g The preset kinematic viscosity threshold is the threshold value corresponding to the target medium being in a preset low viscosity state, and k is the viscosity-temperature coefficient of the target medium.

2. The breather valve with a heat-insulating jacket as described in claim 1, characterized in that: The valve cavity (101) has multiple insulation evaluation areas, including a positive pressure valve disc area, a negative pressure valve disc area, a valve cavity wall area, and an airflow channel area connected to the valve cavity (101). The temperature T i (d) i T h ) is the temperature of the preset heating medium T h Below, the lowest temperature in the multiple insulation evaluation areas.

3. The breather valve with a heat-insulating jacket as described in claim 2, characterized in that: The valve body (100) is provided with an airflow channel (102) communicating with the valve cavity (101). An airflow channel heating sleeve (300) is provided on the outer periphery of the airflow channel (102). A channel heating cavity (301) is formed between the airflow channel heating sleeve (300) and the valve body (100). The channel heating cavity (301) is communicating with the heating medium flow cavity (201).

4. The breather valve with a thermal insulation jacket as described in any one of claims 1 to 3, characterized in that: The valve body (100) is provided with a valve cover (400) on its top. The valve cover (400) includes a valve cover body (401) and an arc-shaped cover (402). The valve cover body (401) covers the top of the valve body (100). The arc-shaped cover (402) is located on the side of the valve cover body (401) away from the valve cavity (101). A valve cover heating cavity (403) is formed between the arc-shaped cover (402) and the valve cover body (401).

5. The breather valve with a heat-insulating jacket as described in claim 4, characterized in that: The valve cover (400) is provided with a negative pressure valve core (500), the negative pressure valve core (500) includes a valve cover (501) located in the valve cavity (101) and a valve stem (502) connected to the valve cover (501). The valve stem (502) passes through the valve cover body (401) and extends into the valve cover heating cavity (403). The valve cover heating chamber (403) is connected to the heating medium flow chamber (201).

6. The breather valve with a heat-insulating jacket as described in claim 5, characterized in that: The arc-shaped cover (402) is provided with a first flow pipe (404) communicating with the valve cover heating chamber (403), and the heat insulation jacket (200) is provided with a second flow pipe (202) communicating with the heating medium flow chamber (201). The first flow pipe (404) and the second flow pipe (202) are spaced apart along the height direction of the valve body (100), and the first flow pipe (404) is located above the second flow pipe (202).

7. The breather valve with a heat-insulating jacket as described in claim 6, characterized in that: The valve cover heating chamber (403) and the heating medium flow chamber (201) are connected by a detachable communication assembly (600). The detachable communication assembly (600) includes a first communication pipe (601) disposed on the arc-shaped cover (402) and connected to the valve cover heating chamber (403), and a second communication pipe (602) disposed on the insulation jacket (200) and connected to the heating medium flow chamber (201). The connection ends of the first communication pipe (601) and the second communication pipe (602) are arranged opposite to each other along the disassembly direction of the valve cover (400) relative to the valve body (100).

8. The breather valve with a heat-insulating jacket as described in claim 7, characterized in that: The first flow pipe (404) has a first extension pipe section (404a) extending into the valve cover heating cavity (403), and the first connecting pipe (601) has a second extension pipe section (601a) extending into the valve cover heating cavity (403). The first extension pipe section (404a) extends into the valve cover heating cavity (403) along the height direction of the valve body (100) for a length of L1, and the second extension pipe section (601a) extends into the valve cover heating cavity (403) along the height direction of the valve body (100) for a length of L2, and L2 > L1.

9. The breather valve with a thermal insulation jacket as described in any one of claims 6 to 8, characterized in that: The projection range of the valve cover heating cavity (403) on the valve cover body (401) along the height direction of the valve body (100) covers the projection range of the valve cavity (101) on the valve cover body (401) along the height direction of the valve body (100).

10. A method for determining the target flow thickness of a breather valve with an insulating jacket, characterized in that: include: Obtain the viscosity-temperature reference parameters of the target medium and the preset kinematic viscosity threshold ν. g and the preset heating medium temperature T h The viscosity-temperature reference parameter includes a reference temperature T. ref The target medium at the reference temperature T ref The kinematic viscosity ν0 and the viscosity-temperature coefficient k of the target medium; Determine the preset heating medium temperature T h And set multiple candidate flow thicknesses d i ; For each of the candidate flow thicknesses d i At the preset heating medium temperature T h Next, the heating medium is introduced into the channel with the corresponding candidate flow thickness d. i The heating medium flow chamber (201) is used to obtain the temperature T corresponding to the valve chamber (101). i (d) i T h ); Determine the candidate flow thickness d i Does it meet the low viscosity insulation condition? The low viscosity insulation condition is satisfied as follows: ， The candidate flow thickness d that satisfies the aforementioned low viscosity heat preservation condition i In the middle, the candidate flow thickness d with the smallest value is selected. i The target flow thickness D is determined, and the target flow thickness D satisfies: ， Among them, d is involved in determining the target flow thickness D. i Candidate flow thickness to meet the low viscosity insulation conditions.

11. The method for determining the target flow thickness as described in claim 10, characterized in that: Obtain the temperature T corresponding to the valve chamber (101). i (d) i T h When ), with the corresponding candidate flow thickness d i Multiple temperature detection points are set on the breathing valve sample. The multiple temperature detection points include a first temperature detection point located in the positive pressure valve disc area, a second temperature detection point located in the negative pressure valve disc area, a third temperature detection point located in the valve cavity wall area, and a fourth temperature detection point located in the airflow channel area. The positive pressure valve disc area temperature T1 is obtained through the first temperature detection point, the negative pressure valve disc area temperature T2 is obtained through the second temperature detection point, the valve cavity wall temperature T3 is obtained through the third temperature detection point, and the airflow channel area temperature T4 is obtained through the fourth temperature detection point. The lowest temperature among the positive pressure valve disc region temperature T1, the negative pressure valve disc region temperature T2, the valve cavity wall temperature T3, and the airflow channel region temperature T4 is determined as the candidate flow thickness d. i At the preset heating medium temperature T h The corresponding temperature T i (d) i T h ).

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