A safety relief valve with a double-acting damping chamber

Abstract

This invention discloses a safety relief valve with a double-acting damping chamber, belonging to the technical field of hydraulic safety valves. It includes a valve body, a flow ring, a valve core, and a compression deformation assembly. Utilizing an optimized design of the flow ring and valve core structure, a three-way mating clearance setting can be achieved between the valve core and the flow ring. Combined with the corresponding formation of the double damping chamber in the flow ring, it effectively prevents the rapid opening or rapid retraction of the valve core, achieving damped control during the opening and closing process of the relief valve. The safety relief valve with a double-acting damping chamber of this invention has a compact structure and is easy to install. It can effectively suppress the vibration amplitude of the valve core during the operation of the safety relief valve, reduce or avoid pressure pulsation caused by excessive valve core amplitude, fully ensure the system stability of the safety relief valve, reduce system noise, and extend the service life of the valve core and valve body. It has good practical value and application prospects.

Description

Technical Field

[0001] This invention belongs to the technical field of hydraulic safety valves, specifically relating to a safety relief valve with a double-acting damping chamber. Background Technology

[0002] A safety relief valve is a pressure control valve that is normally closed. When the pressure of the medium in the hydraulic circuit of the test bench exceeds a certain limit, the safety valve opens to discharge the medium to the outside of the system, thus preventing the pressure of the medium in the circuit from exceeding the limit value.

[0003] Normally, the maximum pressure set by the safety relief valve for the system pipeline is controlled by the pressure regulating spring within the valve. This maximum pressure is the discharge pressure set by the safety relief valve. When the hydraulic pressure at one end of the valve core exceeds the spring force generated by the regulating spring, the valve will open, allowing the medium to pass through the safety relief valve and discharge a portion of the medium in the pipeline, preventing the pressure in the circuit from continuously rising. If the flow rate in the circuit continues to increase, the inlet pressure of the safety relief valve rises, the valve opening widens, and more medium will be discharged from the safety relief valve. Ultimately, the safety relief valve fully opens, discharging all the medium in the circuit through it.

[0004] During the use of safety relief valves, fluctuations in flow rate or the valve's own instability often threaten the safety of pressure-sensitive components, affecting the valve's operational stability and posing a significant challenge to its lifespan. Therefore, relief valves requiring high pressure stability often necessitate the inclusion of damping elements within the valve body to ensure stable operation. However, in existing safety relief valves, the damping elements are often simply a damping orifice of fixed size within the damping chamber, or gap damping achieved through a fixed clearance. These damping elements offer limited effectiveness and cannot adequately guarantee stable operation, thus impacting the valve's stability and long-term usability. Summary of the Invention

[0005] In view of one or more of the above-mentioned defects or improvement needs of the prior art, the present invention provides a safety relief valve with a double-acting damping chamber, which can effectively suppress the vibration amplitude of the valve core during the use of the safety relief valve, reduce the pressure pulsation caused by excessive valve core vibration, improve system stability, and reduce system noise.

[0006] To achieve the above objectives, the present invention provides a safety relief valve with a dual-acting damping cavity, comprising a valve body having a accommodating cavity, wherein a valve core and a compression deformation assembly are accommodated in the accommodating cavity, and a fluid inlet and a fluid outlet are formed on the valve body respectively communicating with the accommodating cavity; one end of the valve core faces the fluid inlet, and the other end is matched with the compression deformation assembly; the compression deformation assembly is used to always apply a force to the valve core pointing towards the fluid inlet, and to change the magnitude of the force borne by the valve core by changing the degree of compression of the compression deformation assembly, thereby realizing the opening and closing of the fluid inlet;

[0007] Corresponding to the valve core, a flow ring is also provided in the accommodating cavity;

[0008] The flow ring has a damping cavity inside and a flow groove at one end; the damping cavity and the flow groove are connected by a first through hole, and a second through hole is provided on the side of the flow ring away from the first through hole, connecting the damping cavity; the flow groove is directly opposite the fluid inlet and can be connected to the fluid inlet after the valve core is disengaged from the fluid inlet; and the flow ring has a plurality of flow holes that respectively connect the flow groove and the accommodating cavity.

[0009] The first through hole, the damping cavity, and the second through hole are coaxially arranged; and

[0010] The valve core includes a guide section and a first connecting section and a second connecting section coaxially disposed at both ends of the guide section. The outer diameter of the two connecting sections is smaller than the outer diameter of the guide section. The valve core passes through the flow ring, and its guide section is fitted into the damping cavity in a gap-matched manner, dividing the damping cavity into a first damping cavity and a second damping cavity. The first connecting section is fitted with the first through hole with a gap, and its end extends into the flow groove and corresponds to the fluid inlet. The second connecting section is fitted with the second through hole with a gap, and its end extends out of the flow ring and matches the compression deformation component.

[0011] As a further improvement of the present invention, the flow ring includes a first ring body and a second ring body coaxially connected at their ends;

[0012] The first ring body has a damping groove and a flow groove at both ends, which are connected by a first through hole;

[0013] The second ring body has a blind hole at one end and a second through hole at the bottom of the blind hole. The two ring bodies are fitted together through the blind hole to the end of the first ring body with a damping groove, thereby forming the damping cavity.

[0014] As a further improvement of the present invention, the accommodating cavity includes a flow passage cavity disposed in the middle of the valve body and an axial through hole opened along the axial direction of the valve body and passing through the flow passage cavity;

[0015] The inner diameter of the flow passage cavity is larger than the inner diameter of the axial through hole; the fluid inlet is formed at one end of the axial through hole, and the compression deformation component is disposed at the other end of the axial through hole; the flow ring is fixed in the flow passage cavity and is disposed along the axial direction of the axial through hole.

[0016] As a further improvement of the present invention, the flow ring is fixed in the flow cavity by a valve seat connected to the end of the axial through hole; and

[0017] The fluid inlet is formed by a through hole coaxially opened in the middle of the valve seat.

[0018] As a further improvement of the present invention, the other end of the flow ring opposite to the valve seat is configured as a stepped shaft and has an annular stepped surface;

[0019] The annular stepped surface abuts against the inner wall surface of the flow passage cavity where it connects to the axial through hole, and the small-diameter end of one side of the annular stepped surface is embedded in the axial through hole in a gap-matching manner.

[0020] As a further improvement of the present invention, the valve seat is a stepped shaft structure, and one end of the axial through hole is set as a stepped hole;

[0021] The valve seat has an external thread on its outer circumference at the large diameter end for threaded connection with the inner wall of the axial through hole; the valve seat has a clearance matching the axial through hole at its small diameter end, and a sealing element is provided on the outer circumference of the small diameter end.

[0022] As a further improvement of the present invention, a pressure regulating component is provided at the end of the axial through hole corresponding to the compression deformation component, for adjusting the magnitude of the force applied to the valve core by adjusting the degree of deformation of the compression deformation component.

[0023] As a further improvement of the present invention, the pressure regulating assembly includes a pressure cap connected to the end of the axial through hole;

[0024] The pressure cap has a threaded through hole in the middle, and an adjusting screw is threaded into it to adjust the compression degree of the compression deformation component by adjusting the screw's screw depth.

[0025] As a further improvement of the present invention, the inner diameter of the first connecting segment is equal to the inner diameter of the second connecting segment;

[0026] and / or

[0027] The fluid inlet is flared at the end opposite the valve core, and the end of the first connecting section is truncated into a cone shape.

[0028] As a further improvement of the present invention, the flow holes are a plurality of holes arranged at circumferential intervals;

[0029] and / or

[0030] The flow area of ​​all the flow holes is not greater than the flow area of ​​the fluid inlet.

[0031] The aforementioned improved technical features can be combined with each other as long as they do not conflict with each other.

[0032] In summary, the beneficial effects of the above-described technical solutions conceived by this invention compared with the prior art include:

[0033] (1) The safety relief valve with double-acting damping chamber of the present invention includes a valve body, a flow ring, a valve core and a compression deformation component. By utilizing the preferred design of the flow ring and valve core structure, a three-fitting gap setting between the valve core and the flow ring can be realized. With the corresponding formation of the double damping chamber in the flow ring, the valve core can be effectively prevented from opening or falling back quickly, thereby realizing damping control of the relief valve opening and closing process, ensuring the reliability of the relief valve during use, effectively suppressing the vibration amplitude of the valve core, reducing the pressure pulsation caused by excessive valve core amplitude, achieving the purpose of improving system stability and reducing system noise, and also effectively avoiding collision between the valve core and valve seat caused by excessive valve core fall, further improving the service life of each component of the relief valve.

[0034] (2) The safety relief valve with double-acting damping chamber of the present invention can effectively simplify the setting process of the compression deformation component by setting the compression deformation component as a spring component and setting two spring seats accordingly, and ensure the reliability and stability of the compression deformation component setting; at the same time, by setting the second spring seat to match the gap of the axial through hole, the reliability of the spring setting can be further guaranteed, and the sealing performance of the valve body end can be effectively improved.

[0035] (3) The safety relief valve with double-acting damping chamber of the present invention has a pressure regulating component set at the end of the axial through hole corresponding to the compression deformation component, so as to adjust the compression degree of the compression deformation component, thereby changing the initial pressure of the compression deformation component acting on the valve core, so as to meet the application requirements of the relief valve under different application requirements, effectively expanding the application range of the safety relief valve, improving the compatibility and versatility of the safety relief valve, and reducing the application cost of the safety relief valve.

[0036] (4) The safety relief valve with double-acting damping chamber of the present invention has a compact structure and is easy to set up. It can effectively suppress the vibration amplitude of the valve core during the operation of the safety relief valve, reduce or avoid pressure pulsation caused by excessive valve core amplitude, fully ensure the system stability of the safety relief valve, reduce system noise, and extend the service life of the valve core and valve body of the safety relief valve. It has good practical value and application prospects. Attached Figure Description

[0037] To more clearly illustrate the technical solutions in the embodiments of the present invention, the accompanying drawings used in the embodiments will be briefly introduced below. 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.

[0038] Figure 1 This is a cross-sectional view of the overall structure of the safety relief valve with a double-acting damping cavity in an embodiment of the present invention;

[0039] Figure 2 This is a schematic diagram of the double-damping cavity flow ring structure of the safety relief valve with double-acting damping cavity in an embodiment of the present invention;

[0040] Figure 3 This is a schematic diagram of the valve core structure of the safety relief valve with a double-acting damping cavity in an embodiment of the present invention;

[0041] In all the accompanying drawings, the same reference numerals denote the same technical features, specifically:

[0042] 1. Valve body; 2. Flow ring; 3. Valve core; 4. Compression deformation assembly; 5. Pressure regulating assembly; 6. Valve seat;

[0043] 101. Flow passage; 102. Axial through hole; 103. Fluid outlet;

[0044] 201. First ring body; 202. Second ring body; 203. Damping groove; 2031. First damping cavity; 2032. Second damping cavity; 204. Flow channel; 205. Flow hole; 206. First through hole; 207. Second through hole;

[0045] 301. Guide section; 302. First connecting section; 303. Second connecting section; 304. Third connecting section;

[0046] 401. Spring; 402. First spring seat; 403. Second spring seat;

[0047] 501, gland; 502, pressure regulating screw; 601, fluid inlet. Detailed Implementation

[0048] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention. Furthermore, the technical features involved in the various embodiments of this invention described below can be combined with each other as long as they do not conflict with each other.

[0049] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0050] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0051] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0052] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0053] Example:

[0054] Please see Figures 1-3 The safety relief valve with a double-acting damping cavity in a preferred embodiment of the present invention includes a valve body 1 having a accommodating cavity. A valve core 3 and a compression deformation assembly 4 are housed within the accommodating cavity. A fluid inlet and a fluid outlet, respectively communicating with the accommodating cavity, are formed on the valve body 1. The valve core 3 can reciprocate axially within the accommodating cavity, with one end facing the fluid inlet and the other end matched with the compression deformation assembly 4. The compression deformation assembly 4 is supported by an elastic material and can undergo compression deformation after being subjected to pressure, generating a restoring force to recover the deformation. This force consistently applies a force to the valve core 3 pointing towards the fluid inlet. By changing the degree of compression of the compression deformation assembly 4, the magnitude of the force on the valve core 3 can be altered, thereby opening and closing the fluid inlet.

[0055] Based on this, by setting a corresponding type of flow ring 2 in the accommodating cavity and optimizing the structure of the valve core 3, the reliable setting of the safety relief valve can be achieved by utilizing the corresponding matching between the valve core 3 and the flow ring 2.

[0056] Specifically, in the preferred embodiment, the accommodating cavity includes a flow passage cavity 101 opened in the middle of the valve body 1, and an axial through hole 102 opened along the axial direction of the valve body 1, which penetrates the flow passage cavity 101. The two are further preferably coaxially arranged, and the inner diameter of the flow passage cavity 101 is larger than the inner diameter of the axial through hole 102.

[0057] Meanwhile, a flow ring 2 is coaxially embedded in the flow cavity 101, which is limited by the valve seat 6 connected to the end of the axial through hole 102, and a valve core 3 is correspondingly provided in the flow ring 2; accordingly, a compressibility variable component 4 is correspondingly provided in the axial through hole 102 at the end of the flow ring 2 away from the valve seat 6, which is used to act on the end of the valve core 3 away from the valve seat 6 and always apply a force to the valve core 3 pointing towards the end of the valve seat 6.

[0058] Specifically, in the preferred embodiment, the valve body 1 is preferably a cylindrical structure, and more preferably a stepped circular shaft structure, including a first shaft segment with a different outer diameter. Figure 1 (lower and middle ends) and second shaft section ( Figure 1 (Middle and upper end), the outer diameter of the first shaft segment is larger than the outer diameter of the second shaft segment, and an annular stepped surface is formed at the connection between the two, such as Figure 1 As shown in the image.

[0059] The flow passage cavity 101 is disposed in the first shaft section, and the axial through hole 102 extends through both shaft sections axially. Simultaneously, one end of the axial through hole 102 is provided with a valve seat 6 for connecting to a device or component receiving fluid, and the through hole in the middle of the valve seat 6 forms the fluid inlet 601 of the safety relief valve. Correspondingly, a fluid outlet 103 communicating with the flow passage cavity 101 is provided on one side of the first shaft section.

[0060] In actual setup, the fluid inlet 601 is coaxially arranged with the axial through hole 102, and the axis of the fluid outlet 103 is preferably perpendicular to the axis of the fluid inlet 601, that is, the axis of the fluid outlet 103 is perpendicular to the axis of the axial through hole 102.

[0061] More specifically, in order to achieve reliable assembly of the valve seat 6 at one end of the axial through hole 102, one end of the axial through hole 102 (the side of the first shaft segment away from the second shaft segment) is set as a stepped hole; correspondingly, the valve seat 6 is set as a matching stepped shaft, so that the two can be abutted and limited by the annular stepped surface.

[0062] For example, in such Figure 1 In the preferred embodiment shown, the valve seat 6 is configured as a two-section structure, with its large-diameter end matched with the axial through hole 102 by a thread. Correspondingly, the small-diameter end of the valve seat 6 is matched with the axial through hole 102 by a clearance; at the same time, it is preferable to have an annular groove circumferentially formed on the outer periphery of the small-diameter end of the valve seat 6, and to embed an annular seal therein, so as to further improve the sealing performance of the assembly between the valve seat 6 and the axial through hole 102.

[0063] Furthermore, the end of the fluid inlet 601 near the flow ring 2 is configured as a flared mouth, that is, the inner diameter of its opening decreases from the outside to the inside; correspondingly, the end of the valve core 3 used to match the valve seat 6 is configured as a matching frustoconical structure, so that the end of the valve core 3 can abut against the flared end of the fluid inlet 601 to temporarily block the fluid inlet 601.

[0064] like Figure 2 As shown, in the preferred embodiment, the flow ring 2 includes a first ring body 201 and a second ring body 202 that can be coaxially connected at their ends, both ring bodies having a cylindrical structure. The first ring body 201 has blind holes of a certain depth coaxially formed at both ends, namely a damping groove 203 and a flow groove 204. The two blind holes are preferably circular, and are further connected by a first through hole 206 formed along the axial direction. Correspondingly, one end of the second ring body 202 has a blind hole of a certain depth formed along the axial direction, and the other end has a through hole connecting to the blind hole, namely a second through hole 207.

[0065] In actual installation, the inner diameter of the first through hole 206 is smaller than the inner diameter of the blind holes connected at both ends. Furthermore, depending on design requirements, the inner diameters of the two blind holes can be the same or different, which will not be elaborated here. In addition, in the preferred embodiment, the inner diameter of the first through hole 206 is preferably the same as the inner diameter of the second through hole 207.

[0066] More specifically, a plurality of flow holes 205 are provided on the inner peripheral wall of the flow channel 204; in actual installation, the flow holes 205 are preferably multiple flow holes 205 that are equally spaced around the flow channel 204. At the same time, the sum of the flow areas of the multiple flow holes 205 is not greater than the flow area of ​​the valve seat 6, that is, the sum of the cross-sectional areas of the multiple flow holes 205 is not greater than the cross-section of the fluid inlet 601.

[0067] Preferably, each flow hole 205 is preferably opened along the radial direction of the first ring body 201, and the plurality of flow holes 205 are preferably evenly arranged around the center of the flow groove 204.

[0068] Furthermore, one end of the first ring 201 with a damping groove 203 is embedded in a blind hole at the end of the second ring 202, and the two rings are connected and matched by threads, that is, threads are respectively provided on the outer periphery of the end of the first ring 201 and the inner periphery of the blind hole at the end of the second ring 202. By fitting the second ring 202, the opening side of the damping groove 203 can be sealed, thereby forming a damping cavity in the middle of the flow ring 2.

[0069] In actual installation, the end connecting the first ring body 201 to the second ring body 202 is configured as a stepped shaft, with a small-diameter end. The length of this small-diameter end is not greater than the depth of the blind hole at the end of the second ring body 202, and both are preferably identical. Correspondingly, the outer diameter of the second ring body 202 is preferably the same as the outer diameter of the middle portion of the first ring body 201, so that after the two are connected at their ends, the outer circumferences of the two ring bodies are flush. Figure 2 As shown in the image.

[0070] More specifically, in the preferred embodiment, the flow ring 2 is embedded in the flow cavity 101, and its axis coincides with the axis of the axial through hole 102. To achieve accurate positioning of the flow ring 2, the end of the second ring body 202 facing away from the first ring body 201 is configured as a stepped shaft, and an annular stepped surface is formed at its end, such as... Figure 2 As shown in the diagram. Thus, during actual assembly, the aforementioned annular stepped surface can correspondingly abut against the interface wall between the flow cavity 101 and the axial through hole 102, as shown in the diagram. Figure 1 As shown in the image.

[0071] Preferably, in order to prevent the flow ring 2 from shifting in the flow cavity 101, the end of the second ring body 202 is matched with the inner wall surface of the axial through hole 102 with a gap, so as to fully ensure the reliability of the flow ring 2.

[0072] Furthermore, the valve seat 6 is configured such that the end of the stepped shaft is embedded in the flow groove 204 of the first annular body 201, and the two are preferably matched with a gap.

[0073] By matching the two ends of the flow ring 2 with the valve body 1 and the valve seat 6, the flow ring 2 can be accurately positioned in the flow cavity 101.

[0074] It is understood that in actual settings, the specific configuration of the aforementioned flow ring 2 is only a preferred embodiment. It can be changed as needed, as long as it can meet the requirements of matching with the valve core 3 and forming a damping cavity and flow groove 204. It will not be elaborated here.

[0075] like Figure 3 As shown, in the preferred embodiment, the valve core 3 corresponds to the flow ring 2 and has a multi-segment structure, including a guide segment 301 located in the middle and a first connecting segment 302 and a second connecting segment 303 located at the two axial ends of the guide segment 301. The outer diameter of the guide segment 301 is larger than the outer diameter of its two connecting segments, causing the valve core 3 to form a stepped shaft structure.

[0076] In a specific configuration, the outer diameter of the guide section 301 is the same as the inner diameter of the damping groove 203, and the two are assembled with a gap, more specifically, a sliding gap assembly. Correspondingly, the outer diameter of the first connecting section 302 is the same as the inner diameter of the first through hole 206, and the two are assembled with a gap; the outer diameter of the second connecting section 303 is the same as the inner diameter of the second through hole 207, and the two are assembled with a gap. Preferably, the outer diameter of the first connecting section 302 is the same as the outer diameter of the second connecting section 303; more preferably, the gap assembly between at least one connecting section and the through hole is a sliding gap assembly.

[0077] In actual assembly, the valve core 3 and the flow ring 2 are assembled as follows: Figure 1 As described above, at this time, the guide segment 301 is embedded in the cavity formed by the damping groove 203 after the two rings are connected. At the same time, the length of the guide segment 301 is less than the depth of the damping groove 203, and further less than 1 / 2 of the depth of the damping groove 203.

[0078] By embedding the guide section 301, the cavity formed by the damping groove 203 is divided into two parts, namely, as shown in the figure. Figure 1 The first damping cavity 2031 and the second damping cavity 2032 shown are illustrated.

[0079] One end of the valve core 3 extends into the flow channel 204 and matches the end of the valve seat 6; correspondingly, the other end of the valve core 3 extends out of the second through hole 207 and matches one end of the compression deformation assembly 4.

[0080] In a preferred embodiment, the compression deformation component 4 is arranged axially along the axial through hole 102, with one end fixed to the end of the axial through hole 102 away from the flow ring 2, and the other end acting on the end of the valve core 3. By utilizing the compression deformation of the compression deformation component 4, a force pointing towards the valve seat 6 is always applied to the valve core 3.

[0081] Depending on the requirements of the configuration, the compression deformation component 4 in the preferred embodiment can be configured in different forms, such as springs, disc springs, elastic elements made of plastic materials, etc., as long as they can provide reaction force through compression deformation.

[0082] For example, in such Figure 1 In the preferred embodiment shown, the compression deformation component 4 is a spring assembly, which includes a spring 401 arranged axially along the valve core 3, and a first spring seat 402 and a second spring seat 403 respectively fixed at its two ends. The first spring seat 402 is connected to the end of the valve core 3, and a third connecting section 304 is coaxially arranged at the end of the second connecting section 303 corresponding to the connection between the two. The outer diameter of the third connecting section 304 is smaller than the outer diameter of the second connecting section 303, and the two form a stepped shaft structure. Correspondingly, a connecting hole is provided axially in the middle of the first spring seat 402 for the embedding and connection of the third connecting section 304.

[0083] Preferably, the connecting hole on the first spring seat 402 is a through hole, the inner diameter of which is equal to the outer diameter of the third connecting section 304, so that the third connecting section 304 can pass through the connecting hole and be matched with it in terms of gap.

[0084] Furthermore, the arrangement of the second spring seat 403 in the axial through hole 102 can take many forms. For example, the second spring seat 403 can be directly connected to the end of the valve body 1 (such as threaded connection, fixed connection with connector, etc.); or, an end cap or cover plate can be connected to the end of the axial through hole 102; or, an axially adjustable pressure regulating component 5 can be coaxially arranged at the end of the axial through hole 102, so as to adjust the deformation size of the compression deformation component 4 by changing the axial position of the second spring seat 403.

[0085] In a specific preferred embodiment, a pressure adjusting component 5 is provided at the end of the axial through hole 102. It is preferably a pressure screw that is threadedly connected to the end of the axial through hole 102, and the length of the thread at the end of the axial through hole 102 is greater than the length of the pressure screw. By changing the screw insertion depth, the position of the second spring seat 403 can be adjusted accordingly.

[0086] In another preferred embodiment, the voltage regulating component 5 is configured as follows: Figure 1As shown in the figure, at this time, it includes a pressure cap 501 and a pressure adjusting screw 502. The pressure cap 501 is threadedly connected to the end of the axial through hole 102, and a through hole is opened in the middle along the axial direction, so that the pressure adjusting screw 502 is threadedly connected to the through hole. By changing the screw position of the pressure adjusting screw 502, the position of the second spring seat 403 can be changed accordingly.

[0087] More preferably, the outer periphery of the second spring seat 403 is assembled with the axial through hole 102 in a clearance-matched manner, in which case the second spring seat 403 constitutes a piston structure in the axial through hole 102. Accordingly, in order to improve the sealing performance of the match between the second spring seat 403 and the axial through hole 102, a sealing element is provided between the two, which is opened circumferentially, and more preferably disposed in an embedded groove opened circumferentially on the outer periphery of the second spring seat 403.

[0088] By sliding the second spring seat 403 with the axial through hole 102, and connecting the first spring seat 402 with the end of the valve core 3, the axiality of the spring 401 in setting and operation can be effectively guaranteed, and the torsion and bending of the spring can be avoided.

[0089] Furthermore, in actual installation, the valve port of the safety relief valve in the preferred embodiment can be a ball valve, cone valve, or flat valve, which will not be elaborated here. Meanwhile, in the preferred embodiment, the flow ring 2 is preferably made of metal, and the valve core 3 is preferably made of engineering plastic with self-lubricating properties. This effectively reduces the friction between the valve core 3 and the flow ring 2, thereby preventing jamming when the valve core 3 and the flow ring 2 move relative to each other. Correspondingly, the valve seat 6 in the preferred embodiment is also preferably made of engineering plastic with low hardness, forming a soft-hard fit with the valve core 3, which can significantly improve the sealing performance of the relief valve.

[0090] For the safety relief valve in the preferred embodiment, the damping effect of the valve core 3 is mainly formed by the three mating gaps between the valve core 3 and the flow ring 2 and the double damping cavity.

[0091] Specifically, when the fluid pressure at the fluid inlet 601 reaches the set opening pressure, the safety relief valve opens. The fluid pressure in the fluid inlet 601 pushes the valve core 3 against the force of the compression deformation component 4 and moves it away from the fluid inlet 601. At this time, the volume of the first damping chamber 2031 increases, and the pressure therein decreases and becomes lower than the external pressure. Correspondingly, the first damping chamber 2031 draws in the medium and experiences greater resistance, thus hindering the rapid opening of the valve core 3. In contrast, the volume of the second damping chamber 2032 decreases, and the pressure therein increases and becomes higher than the external pressure, thereby producing a damping effect on the valve core 3. Since the valve core 3 is subjected to a force directed towards the compression deformation component 4, the damping effect of the valve core 3 can be further enhanced, thereby ensuring the stability of the valve core 3 when it opens.

[0092] Under conditions of high external pressure and low pressure in the first damping chamber 2031, some medium will enter the first damping chamber 2031 and the second damping chamber 2032 from the outside through the gap between the valve core 3 and the flow ring 2, ensuring that the first damping chamber 2031 and the second damping chamber 2032 will only "hinder but not stop" the movement of the valve core 3.

[0093] When the valve opening reaches its maximum or the pressure at the fluid inlet 601 decreases, the valve core 3 moves towards the valve seat 6 under the action of the compression deformation component 4, causing the volume of the second damping chamber 2032 to increase and the pressure to decrease, falling below the external pressure. At this time, the second damping chamber 2032 draws in the medium, while the volume of the first damping chamber 2031 decreases, and the pressure rises, exceeding the external pressure. The valve core 3 is subjected to a reaction force from the first damping chamber 2031 pointing towards the compression deformation component 4, thus hindering the rapid return of the valve core 3. Under the condition of high pressure in the first damping chamber 2031 and low external pressure, some medium will open the second damping chamber 2032 through the gap between the valve core 3 and the flow ring 2, ensuring that the first damping chamber 2031 and the second damping chamber 2032 only "hinder but do not prevent" the movement of the valve core 3.

[0094] By adaptively adjusting the dual damping chambers, the vibration amplitude of the valve core 3 can be effectively suppressed, reducing pressure pulsation caused by excessive amplitude of the valve core 3, thereby improving system stability and reducing system noise. At the same time, it can prevent impact damage caused by the rapid return of the valve core 3 to the valve seat 6, further extending the lifespan of the valve core 3 and the valve seat 6.

[0095] The safety relief valve with a double-acting damping chamber in this invention has a compact structure and is easy to set up. It can effectively suppress the vibration amplitude of the valve core during the operation of the safety relief valve, reduce or avoid pressure pulsation caused by excessive valve core amplitude, fully ensure the system stability of the safety relief valve, reduce system noise, and extend the service life of the valve core and valve body of the safety relief valve. It has good practical value and application prospects.

[0096] Those skilled in the art will readily understand that the above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A safety relief valve with a dual-acting damping cavity, comprising a valve body having a accommodating cavity, wherein a valve core and a compression deformation assembly are accommodated in the accommodating cavity, and a fluid inlet and a fluid outlet are formed on the valve body respectively communicating with the accommodating cavity; one end of the valve core faces the fluid inlet, and the other end is matched with the compression deformation assembly; the compression deformation assembly is used to always apply a force to the valve core pointing towards the fluid inlet, and to change the magnitude of the force borne by the valve core by changing the degree of compression of the compression deformation assembly, thereby realizing the opening and closing of the fluid inlet; characterized in that, Corresponding to the valve core, a flow ring is also provided in the accommodating cavity; The flow ring has a damping cavity inside and a flow groove at one end; the damping cavity and the flow groove are connected by a first through hole, and a second through hole is provided on the side of the flow ring away from the first through hole, connecting the damping cavity; the flow groove is directly opposite the fluid inlet and can be connected to the fluid inlet after the valve core is disengaged from the fluid inlet; and the flow ring has a plurality of flow holes that respectively connect the flow groove and the accommodating cavity. The first through hole, the damping cavity, and the second through hole are coaxially arranged; and The valve core includes a guide section and a first connecting section and a second connecting section coaxially disposed at both ends of the guide section. The outer diameter of the two connecting sections is smaller than the outer diameter of the guide section. The valve core passes through the flow ring, and its guide section is assembled in the damping cavity in a gap-matched manner, dividing the damping cavity into a first damping cavity and a second damping cavity. The first connecting section is gap-fitted with the first through hole, and its end extends into the flow groove and corresponds to the fluid inlet; the second connecting section is gap-fitted with the second through hole, and its end extends out of the flow ring and matches the compression deformation component.

2. The safety relief valve with a double-acting damping chamber according to claim 1, characterized in that, The flow ring includes a first ring body and a second ring body that are coaxially connected at their ends; The first ring body has a damping groove and a flow groove at both ends, which are connected by a first through hole; The second ring body has a blind hole at one end and a second through hole at the bottom of the blind hole. The two ring bodies are fitted together through the blind hole to the end of the first ring body with a damping groove, thereby forming the damping cavity.

3. The safety relief valve with a double-acting damping chamber according to claim 1, characterized in that, The accommodating cavity includes a flow passage cavity disposed in the middle of the valve body and an axial through hole that is opened along the axial direction of the valve body and penetrates the flow passage cavity; The inner diameter of the flow passage cavity is larger than the inner diameter of the axial through hole; the fluid inlet is formed at one end of the axial through hole, and the compression deformation component is disposed at the other end of the axial through hole; the flow ring is fixed in the flow passage cavity and is disposed along the axial direction of the axial through hole.

4. The safety relief valve with a double-acting damping chamber according to claim 3, characterized in that, The flow ring is fixed in the flow cavity by a valve seat connected to the end of the axial through hole; and The fluid inlet is formed by a through hole coaxially opened in the middle of the valve seat.

5. The safety relief valve with a double-acting damping chamber according to claim 4, characterized in that, The other end of the flow ring opposite to the valve seat is configured as a stepped shaft and has an annular stepped surface; The annular stepped surface abuts against the inner wall surface of the flow passage cavity where it connects to the axial through hole, and the small-diameter end of one side of the annular stepped surface is embedded in the axial through hole in a gap-matching manner.

6. The safety relief valve with a double-acting damping chamber according to claim 4, characterized in that, The valve seat has a stepped shaft structure, and one end of the axial through hole is set as a stepped hole. The valve seat has an external thread on its outer circumference at the large diameter end for threaded connection with the inner wall of the axial through hole; the valve seat has a clearance matching the axial through hole at its small diameter end, and a sealing element is provided on the outer circumference of the small diameter end.

7. The safety relief valve with a double-acting damping cavity according to any one of claims 3 to 6, characterized in that, A pressure regulating component is provided at the end of the axial through hole corresponding to the compression deformation component, which is used to adjust the magnitude of the force applied to the valve core by adjusting the degree of deformation of the compression deformation component.

8. The safety relief valve with a double-acting damping cavity according to claim 7, characterized in that, The pressure regulating assembly includes a pressure cap connected to the end of the axial through hole; The pressure cap has a threaded through hole in the middle, and an adjusting screw is threaded into it to adjust the compression degree of the compression deformation component by adjusting the screw's screw depth.

9. The safety relief valve with a double-acting damping cavity according to any one of claims 1 to 6 and 8, characterized in that, The inner diameter of the first connecting segment is equal to the inner diameter of the second connecting segment; and / or The fluid inlet is flared at the end opposite the valve core, and the end of the first connecting section is truncated into a cone shape.

10. The safety relief valve with a double-acting damping cavity according to any one of claims 1 to 6 and 8, characterized in that, The flow holes are multiple ones arranged at circumferential intervals; and / or The flow area of ​​all the flow holes is not greater than the flow area of ​​the fluid inlet.

Images