Anti-surge anti-blocking angle valve

Abstract

This invention relates to the field of angle valves, specifically to an anti-surge and anti-clogging angle valve. The angle valve includes a valve body, a valve cover, a sleeve, a valve core, and an actuator. The valve body has a central cavity and inlet and outlet channels that are perpendicular to each other and connected to the central cavity. The valve cover covers the end of the central cavity furthest from the inlet channel. The sleeve is installed inside the central cavity, coaxially arranged with the inlet channel, and has a small orifice section and a large orifice section along the axial direction. The peripheral wall of the small orifice section has multiple small liquid outlet holes, and the peripheral wall of the large orifice section has multiple large liquid outlet holes. The small orifice section is closer to the inlet channel than the large orifice section. The valve core is slidably installed inside the sleeve and can slide away from the inlet channel to avoid some of the large liquid outlet holes. The actuator is connected to the valve core and is used to drive the valve core to move towards the inlet channel to close the inlet channel and to drive the valve core away from the inlet channel to open the inlet channel. This invention can effectively reduce fluid vibration and noise within the angle valve, prevent surge in the applied pipeline, and simultaneously address vibration and noise reduction as well as anti-clogging issues.

Description

Technical Field

[0001] This invention relates to the field of angle valves, and more specifically to an anti-surge and anti-blockage angle valve. Background Technology

[0002] A conventional angle valve (angle gate valve) includes a valve body, a valve cover, a valve core, and an actuator. The valve body has a central cavity, an inlet channel, and an outlet channel. The inlet channel and the outlet channel are perpendicular to each other and connected through the central cavity. The valve cover is mounted on the valve body. The valve core is slidably installed in the central cavity. The actuator is connected to the valve core. When the valve core is driven downward to block the inlet channel, the valve closes. When the valve core is driven upward to open the inlet channel, the valve opens. Fluid enters the central cavity from the inlet channel and then flows out from the outlet channel.

[0003] Patents such as CN202320468288.X (sealing device for angle stop valve) and CN201720996368.7 (angle stop valve) both employ the aforementioned structure. In angle valves with this structure, the high flow rate and large pressure difference during fluid flow from the central cavity into the inlet channel generate significant vibration and noise. Angle valves are commonly used in pipelines of heat pump compressors, etc. Therefore, the vibration and noise of the angle valve can cause surge in the pipeline, thereby affecting the pressure, flow rate, and other characteristics of the pipeline. Summary of the Invention

[0004] The technical problem to be solved by the present invention is to overcome the defects of the prior art and provide an anti-surge and anti-blockage angle valve, which can effectively reduce the vibration and noise of fluid in the angle valve, prevent surge in the pipeline to which it is applied, and can take into account both vibration reduction, noise reduction and anti-blockage problems.

[0005] To solve the above-mentioned technical problems, the technical solution of the present invention is: an anti-surge and anti-blockage angle valve, comprising a valve body, a valve cover, a valve core, and an actuator; the valve body has a central cavity and an inlet flow channel and an outlet flow channel that are respectively connected to the central cavity and perpendicular to each other; the valve cover is installed on the end of the central cavity away from the inlet flow channel;

[0006] The anti-surge and anti-clogging angle valve also includes a sleeve, which is installed in the central cavity and coaxially arranged with the inlet channel. The sleeve has a small orifice section and a large orifice section along the axial direction. The peripheral wall of the small orifice section has multiple small liquid outlet holes, and the peripheral wall of the large orifice section has multiple large liquid outlet holes. The small orifice section is closer to the inlet channel than the large orifice section.

[0007] The valve core is slidably installed inside the sleeve and can slide away from the inlet channel to avoid part of the large outlet hole; the actuator is connected to the valve core and is used to drive the valve core to move toward the inlet channel to close the inlet channel and to drive the valve core to move away from the inlet channel to open the inlet channel;

[0008] A circumferential space is provided between the outer peripheral wall of the sleeve and the peripheral wall of the middle cavity, and the size of the space matches the outflow channel. When the valve core is in the open position of the inflow channel, the fluid enters the sleeve from the inflow channel, then enters the space from the small outlet hole and the large outlet hole, and finally exits from the outflow channel.

[0009] Furthermore, to further reduce noise, the inner diameter of the inlet channel is smaller than the inner diameter of the outlet channel.

[0010] To further ensure a reliable seal over a long period, the anti-surge and anti-clogging angle valve also includes a valve seat sealing pair. This valve seat sealing pair is installed at the junction of the inlet flow channel and the central cavity, and includes a rigid valve seat and a flexible valve seat. The rigid valve seat is installed within the central cavity and has an insert groove, and the flexible valve seat is embedded within the insert groove.

[0011] The hard valve seat is used to contact the valve core to achieve a hard seal, and the surface of the hard valve seat that contacts the valve core is a conical surface; the soft valve seat is used to contact the valve core to achieve a soft seal.

[0012] The rigid valve seat has a flange extending beyond the soft valve seat along the central axis of the inlet flow channel.

[0013] To further reduce the processing difficulty of the sleeve, the sleeve has two parts, namely an upper sleeve and a lower sleeve. The upper sleeve and the lower sleeve are axially sealed and spliced ​​together. The small hole section and the large hole section are both set on the lower sleeve.

[0014] To further improve the reliability of the seal between the two sleeves, a spring-loaded sealing ring is provided between the upper and lower sleeves, and at least one sleeve has a guide band on its inner circumferential wall for guiding the movement of the valve core.

[0015] Furthermore, the diameter of the small liquid outlet is 2.99-3.01 mm, and the diameter of the large liquid outlet is 4.99-5.01 mm;

[0016] Alternatively, the diameter of the small outlet hole may be 4.99-5.01 mm, and the diameter of the large outlet hole may be 7.99-8.01 mm.

[0017] Furthermore, in order to reduce the weight of the valve core and extend its service life, the valve core includes a circumferential side plate and end plates disposed at both ends of the circumferential side plate, and each end plate is provided with a balance hole at a non-edge position.

[0018] Furthermore, in order to protect the valve core, a limiting pad is provided on the end face of the valve core facing the valve cover for abutting against the valve cover.

[0019] Furthermore, in order to achieve a double seal, the valve cover is pressed against the valve body and the sleeve respectively, and sealing gaskets are respectively provided between the valve cover and the valve body and between the valve cover and the sleeve.

[0020] Furthermore, in order to maintain a relatively constant flow rate within the valve body and avoid pipe surge, the offset dimension of the central cavity peripheral wall relative to the outer peripheral wall of the sleeve is specified when W ≥ 1 / 4 inch. The distance between the inner cavity wall and the outer sleeve wall at a 45° angle opposite to the outflow channel is a = W, and the distance between the inner cavity wall and the outer sleeve wall at a 45° angle close to the outflow channel is b = 3W.

[0021] When W < 1 / 4 inch, the offset dimension o of the central cavity peripheral wall relative to the outer peripheral wall of the sleeve is 0.0; wherein,

[0022]

[0023] In the formula, D oi The value of h represents the inner diameter of the outlet flow channel; h represents the larger of the valve stroke and the inner diameter of the outlet flow channel.

[0024] Furthermore, when W < 1 / 6 inch, the inner diameter D of the central cavity g Compared to the outer diameter D of the sleeve o 1 inch larger;

[0025] When 1 / 6 inch ≤ W < 1 / 4 inch, the inner diameter D of the cavity g Compared to the outer diameter D of the sleeve o Large 6W.

[0026] By adopting the above technical solution, this invention provides liquid outlet holes on the peripheral wall of the sleeve, changing the concentrated jet of a large hole into a diffused flow of multiple small holes. This gradually consumes the fluid energy passing through the liquid outlet holes, continuously changing the fluid direction, reducing the fluid velocity, controlling the pressure, and decreasing vibration and noise. This invention also provides small liquid outlet holes near the inlet channel of the sleeve and large liquid outlet holes slightly away from the inlet channel. If impurity particles entering the inlet channel block the small liquid outlet holes, they will be pushed out through the large liquid outlet holes by the flowing fluid. This allows the diameter of the small liquid outlet holes to be smaller, not limited by the size of the impurity particles, achieving better vibration and noise reduction. This effectively reduces fluid vibration and noise within the angle valve, preventing surge in the pipeline where the angle valve is used, and also solves the problem of not being able to simultaneously achieve vibration and noise reduction and anti-clogging. Attached Figure Description

[0027] Figure 1 This is a schematic diagram of the anti-surge and anti-blockage angle valve of the present invention;

[0028] Figure 2 This is a cross-sectional view of the sleeve with a large outlet hole and a small outlet hole of the anti-surge and anti-blockage angle valve of the present invention.

[0029] Figure 3 This is a front view of the sleeve with a large outlet hole and a small outlet hole of the anti-surge and anti-blockage angle valve of the present invention;

[0030] Figure 4 for Figure 1 Enlarged view of part A;

[0031] Figure 5 for Figure 1 Enlarged view of part B;

[0032] Figure 6 This is a schematic diagram of the valve core structure of the present invention;

[0033] Figure 7 This is a schematic diagram of the valve body of the present invention;

[0034] Figure 8 This is a schematic diagram of the valve cover structure of the present invention;

[0035] Figure 9 This is a simplified diagram showing the positions of the central cavity peripheral wall and the outer peripheral wall of the sleeve when they are offset according to the present invention;

[0036] In the diagram, 1. Valve body; 11. Middle cavity; 12. Inlet flow channel; 13. Outlet flow channel; 2. Valve cover; 3. Sleeve; 31. Small orifice section; 311. Small liquid outlet hole; 32. Large orifice section; 321. Large liquid outlet hole; 4. Valve core; 41. Circumferential side plate; 42. End plate; 421. Balance hole; 5. Actuator; 6. Valve seat sealing pair; 61. Hard valve seat; 611. Flange; 62. Soft valve seat; 63. O-ring; 7. Spring energy storage sealing ring; 8. Guide band; 9. Sealing gasket; 10. Valve stem. Detailed Implementation

[0037] To make the content of this invention easier to understand, the invention will be further described in detail below with reference to specific embodiments and accompanying drawings.

[0038] like Figures 1 to 9 As shown, an anti-surge and anti-blockage angle valve includes a valve body 1, a valve cover 2, a valve core 4, and an actuator. The valve body 1 has a central cavity 11 and an inlet flow channel 12 and an outlet flow channel 13 that are respectively connected to the central cavity 11 and perpendicular to each other. The valve cover 2 is installed on the end of the central cavity 11 away from the inlet flow channel 12.

[0039] The anti-surge and anti-blockage angle valve also includes a sleeve 3, which is installed inside the central cavity 11 and coaxially arranged with the inlet channel 12. The sleeve 3 has a small orifice section 31 and a large orifice section 32 along its axial direction. The peripheral wall of the small orifice section 31 is provided with multiple small liquid outlet holes 311, and the peripheral wall of the large orifice section 32 is provided with multiple large liquid outlet holes 321. The small orifice section 31 is closer to the inlet channel 12 than the large orifice section 32.

[0040] The valve core 4 is slidably installed inside the sleeve 3 and can slide away from the inlet channel 12 to avoid part of the large outlet hole 321; the actuator 5 is connected to the valve core 4 and is used to drive the valve core 4 to move toward the inlet channel 12 to close the inlet channel 12 and to drive the valve core 4 to move away from the inlet channel 12 to open the inlet channel 12.

[0041] A circumferential space is provided between the outer peripheral wall of the sleeve 3 and the peripheral wall of the middle cavity 11, and the size of the space matches the outlet flow channel 13. When the valve core is in the open position of the inlet flow channel 12, the fluid enters the sleeve 3 from the inlet flow channel 12, then enters the space from the small outlet hole 311 and the large outlet hole 321, and finally exits from the outlet flow channel 13.

[0042] Specifically, liquid outlet holes are provided on the peripheral wall of sleeve 3, changing the concentrated jet of a large hole into a diffused jet of multiple small holes, so that the fluid energy passing through the valve cage is gradually consumed, the fluid direction is constantly changed, the fluid velocity is reduced, the pressure is controlled, and the noise is reduced.

[0043] Furthermore, while a smaller outlet diameter generally results in better vibration and noise reduction, the size of the outlet is determined by both the desired noise level and the size of impurity particles in the pipe. If the outlet is too small, although it can achieve good vibration and noise reduction, it may lead to blockage. Conversely, if the outlet diameter is too large, it won't block, but the vibration and noise reduction effect will be worse. In other words, the particle size of the impurities limits the outlet diameter, making it impossible to simultaneously address both vibration and noise reduction and blockage prevention. Based on this, in this embodiment, a small outlet hole 311 is provided in the part of the sleeve 3 near the inlet channel 12, and a large outlet hole 321 is provided in the sleeve 3 slightly away from the inlet channel 12. If impurity particles entering the inlet channel 12 block the small outlet hole 311, they will be pushed out through the large outlet hole 321 by the flowing fluid. Thus, the diameter of the small outlet hole 311 is not limited by the size of the impurity particles and can be made smaller, achieving better vibration and noise reduction. This can effectively reduce the vibration and noise of the fluid in the angle valve, thereby preventing surge in the pipelines of heat pump compressors and other components used in the angle valve. It also solves the problem that vibration and noise reduction and anti-clogging cannot be achieved simultaneously.

[0044] It should be noted that for higher noise reduction requirements, stepped orifice sleeves, double-layer sleeves, etc., can also be designed. The orifice diameter of the large outlet orifice 321 is determined according to the particle size of the impurities that need to pass through. The fluid entering the inlet channel 12 has been filtered at the front end and will not contain too many impurities.

[0045] In this embodiment, as Figure 8 As shown, the valve cover 2 is spherical, which allows for better pressure bearing and more even distribution of pressure across the valve cover 2 housing. Compared to a flat valve cover, the spherical valve cover 2 exhibits better pressure-bearing performance. The spherical valve cover 2 also allows for a larger volume within the valve cavity, providing a greater stroke for the valve and reducing its size and weight.

[0046] In this embodiment, as Figure 1 and Figure 6 As shown, the actuator 5 is connected to the valve core 4 via the valve stem 10. Packing material is filled between the valve stem 10 and the valve body 1, and is compressed by a disc spring, providing sustained pressure, preventing leakage, and reducing maintenance costs. The disc spring bears static or dynamic loads acting axially at its upper inner edge and lower outer edge. After being compressed, it deforms until flattened, storing energy as a live load. When necessary, this energy is automatically converted into the additional compressive load required for sealing, reducing the continuous compression requirements of the packing during use and minimizing unnecessary downtime and leakage losses. After deforming under load, the disc spring stores a certain amount of potential energy. When the bolts connecting the valve cover 2 and the bolts used to compress the disc spring and packing loosen, the disc spring releases some of this potential energy to maintain pressure to meet sealing requirements. The stress distribution of the disc spring decreases uniformly from the inside out, achieving a low-stroke, high-compensation-force effect.

[0047] In one embodiment, such as Figure 1 As shown, the inner diameter of the inlet channel 12 is smaller than the inner diameter of the outlet channel 13. This further reduces valve noise.

[0048] In one embodiment, such as Figure 1 and Figure 4 As shown, the anti-surge and anti-blockage angle valve also includes a valve seat sealing pair 6, which is installed at the junction of the inlet flow channel 12 and the intermediate cavity 11. The valve seat sealing pair 6 includes a hard valve seat 61 and a soft valve seat 62. The hard valve seat 61 is installed in the intermediate cavity 11 and has an embedding groove, while the soft valve seat 62 is embedded in the embedding groove.

[0049] The hard valve seat 61 is used to contact the valve core 4 to achieve a hard seal, and the surface of the hard valve seat 61 that contacts the valve core 4 is a conical surface. The soft valve seat 62 is used to contact the valve core 4 to achieve a soft seal.

[0050] The rigid valve seat 61 has a flange 611 extending beyond the soft valve seat 62 toward the central axis of the inlet flow channel 12.

[0051] Specifically, the material of the flexible valve seat 62 has a certain degree of elasticity, and compared to the hard valve seat 61, it has lower requirements for machining precision and better sealing performance. An O-ring 63 is also provided between the flexible valve seat 62 and the hard valve seat 61. The O-ring 63 and the flexible valve seat 62 are integrally embedded in the hard valve seat 61, which can be a metal valve seat. In this embodiment, the valve seat sealing pair 6 adopts a double-seal design with sealing by both the hard valve seat 61 and the flexible valve seat 62. The hard valve seat 61 provides support, preventing the flexible valve seat 62 from being crushed due to excessive pressure. The flexible valve seat 62 is supported by the elastic O-ring and protected by the hard valve seat 61. The hard valve seat 61 also prevents the flexible valve seat 62 from overloading, resulting in excellent sealing performance and a longer service life. In the fully closed state, the sealing of the hard valve seat 61 and the flexible valve seat 62 work simultaneously, ensuring a tight and reliable seal; in the fully open state, the flexible valve seat 62 regains its elasticity.

[0052] Furthermore, under normal circumstances, at the instant the valve is opened, the rapid turbulence generated by the medium at the outer edge of the seal can cause vibration of the seal, leading to fatigue failure of the sealing material. In this embodiment, the rigid valve seat 61 has a flange 611 extending beyond the soft valve seat 62 along the central axis of the inlet flow channel 12. Due to the protection of the flange 611, the soft valve seat 62 is not subject to fluid erosion and is less prone to damage.

[0053] Furthermore, the valve seat sealing structure is even more crucial for fluid media containing solid particles. This is primarily because solid particles in the medium can easily become lodged between the sealing surfaces of the valve core 2 and the valve seat, hindering the valve seat seal and causing leakage. Subsequently, the high-speed scouring of the medium can erode and damage the valve seat surface. However, in this embodiment, even if such particles become lodged between the valve core 4 and the rigid valve seat 61, there will be no harm, as the seal between the valve core 4 and the flexible valve seat 61 still provides a reliable and effective supplementary seal.

[0054] In one embodiment, such as Figure 1 and Figure 5 As shown, there are two sleeves 3, namely an upper sleeve and a lower sleeve. The upper sleeve and the lower sleeve are axially sealed and spliced ​​together. The small hole section 31 and the large hole section 32 are both set on the lower sleeve.

[0055] This reduces the length of a single sleeve 3, making it easier to process. It also allows for better large-hole operations on a shorter sleeve 3.

[0056] In one embodiment, such as Figure 1 and Figure 5 As shown, a spring-loaded sealing ring 7 is provided between the two sleeves 3, and at least one sleeve 3 has a guide band 8 on its inner peripheral wall for guiding the movement of the valve core 4.

[0057] In one embodiment, the diameter of the small liquid outlet 311 is 2.99-3.01 mm, and the diameter of the large liquid outlet 321 is 4.99-5.01 mm.

[0058] Alternatively, the diameter of the small outlet hole 311 may be 4.99-5.01 mm, and the diameter of the large outlet hole 321 may be 7.99-8.01 mm.

[0059] It should be noted that the diameter of the small outlet hole 311 is determined according to the noise reduction requirements, while the diameter of the large outlet hole 321 is determined according to the size of the impurity particles.

[0060] For the spring-loaded sealing ring 7, when the sealing ring is installed in the sealing groove, the spring is compressed, causing the jacket lip to press tightly against the sealing groove, thereby forming a seal. The spring provides permanent elasticity to the sealing jacket and compensates for material wear and misalignment or eccentricity of mating parts. The system pressure valve inlet and outlet pressures also assist the sealing jacket in storing energy. Through the spring force assisted by system pressure, effective sealing can be achieved under both high and low pressure. The geometry of the sealing ring installed in the sealing groove also avoids the torsion or spiral failure problems common to O-rings. Under pressure, the PTFE material in the sealing ring easily flows into the engagement gap. Dynamic reciprocating motion increases engagement. Under static conditions, when the pressure, temperature, and engagement gap are below a certain limit, engagement will stop once the pressure generated by friction in the engagement gap equals the system pressure.

[0061] The guide belt 8 serves to prevent wear between the valve core 4 and the sleeve 3, and to protect the spring energy storage sealing ring 7. It possesses excellent heat resistance, corrosion resistance, and friction resistance, and can readily absorb radial changes in vibration performance. The guide belt offers the following advantages: low friction force; good dustproof effect; ability to compensate for gap forces; wear resistance and long service life; ability to withstand mechanical vibration; prevention of metal-to-metal contact; absorption of lateral loads; and a centering effect that increases the extrusion gap of the seal.

[0062] In one embodiment, such as Figure 1 and Figure 6 As shown, the valve core 4 includes a circumferential side plate 41 and end plates 42 disposed at both ends of the circumferential side plate 41. Each end plate 42 is provided with a balance hole 421 at a non-edge position.

[0063] The valve core 4 of this structure is hollow, which can reduce the weight of the entire angle valve. In addition, the end plate 42 is provided with a balance hole 421, which can make the pressure inside the valve core 4 equal with that at the inlet flow channel 12, avoid the valve core 4 from being deformed by pressure, and also prevent the inner side of the valve core 4 from directly facing the fluid impact.

[0064] In one embodiment, such as Figure 1 and Figure 6As shown, the end face of the valve core 4 facing the valve cover 2 is provided with a limiting pad 43 for abutting against the valve cover 2.

[0065] Specifically, during the rising process of valve core 4, if the limit switch of actuator 5 malfunctions, the limit pad 43 directly abuts against valve cover 2, acting as a buffer to protect valve core 4 and the root of valve stem 10.

[0066] In one embodiment, such as Figure 1 As shown, the valve cover 2 is pressed against the valve body 1 and the sleeve 3 respectively, and sealing gaskets 8 are respectively provided between the valve cover 2 and the valve body 1 and between the valve cover 2 and the sleeve 3.

[0067] Specifically, the sealing gasket 8 between the valve cover 2 and the sleeve 3 can prevent internal leakage, and the sealing gasket 8 between the valve cover 2 and the valve body 1 can prevent external leakage.

[0068] In addition, guide sections are designed between valve cover 2 and sleeve 3, and between sleeve 3 and valve body 1, which effectively facilitates alignment and prevents displacement during component assembly. A gap is also designed between sleeve 3 and valve cover 2 to effectively prevent inconsistent thermal expansion and deformation between pressure-bearing components such as valve cover 2 and valve body 1 and internal valve components such as sleeve 3 during valve thermal expansion and contraction, providing radial dimensional compensation for potential thermal expansion deformation. During valve assembly, it is best to fully compress the gasket to minimize misalignment between sliding parts. The compressive load of a spirally wound gasket is the lowest, exceeding the load required for sealing and the rebound force on the sealing element. Bolt load and gasket load need to be calculated according to standard formulas.

[0069] In one embodiment, when W ≥ 1 / 4 inch, the offset dimension of the peripheral wall of the cavity 11 relative to the outer peripheral wall of the sleeve 3 is... The distance a = W between the peripheral wall of the cavity 11 and the outer peripheral wall of the sleeve 3 at a 45° angle opposite to the outlet channel 13, and the distance b = 3W between the peripheral wall of the cavity 11 and the outer peripheral wall of the sleeve 3 at a 45° angle near the outlet channel 13, as detailed below. Figure 9 As shown;

[0070] When W < 1 / 4 inch, the offset dimension o of the peripheral wall of the central cavity 11 relative to the outer peripheral wall of the sleeve 3 is 0.0; where,

[0071]

[0072] In the formula, D oi The value of h represents the inner diameter of the outflow channel 13; h represents the larger of the valve stroke and the inner diameter of the outflow channel 13.

[0073] X is the shortest distance between the circumferential wall of the cavity 11 and the outer circumferential wall of the sleeve 3, and the minimum value of X is 0.5 inches.

[0074] Specifically, if the dimensions formed by the cavity 11 and the sleeve 3 are unsuitable and do not match the outflow channel 13, the valve will have higher flow resistance, failing to meet the valve's Cv flow coefficient, thus leading to noise and vibration problems. Through the formula calculation in this embodiment, it can be ensured that the dimensions of the cavity 11 match the outflow channel 13, maintaining a relatively constant flow velocity in the valve body 1, thereby reducing noise and vibration and further preventing pipeline surge.

[0075] The design of the cavity 11 in valve body 1 can be either concentric or eccentric. An eccentric design results in a smaller diameter for the cavity 11, thus reducing the size of the valve body casting while maintaining flow rate. The wall thickness and flow channel diameter decrease with the offset of the cavity 11, and the thickness of the top and bottom of the valve body 1 is also affected; a smaller diameter flow channel results in a thinner top and bottom of the valve body 1. This eccentric cavity 11 design is easily achieved in casting, but requires additional machining in forging. Smaller valves typically use a concentric cavity design because the cost savings may be negligible. Eccentric cavities 11 are generally used in larger valves and are manufactured using casting. Furthermore, an eccentric cavity 11 allows for the design of the largest possible Cv flow coefficient within the smallest possible volume. Additionally, the eccentricity of the cavity 11, with most of the cavity 11 located at the outlet flow channel 13, can further reduce noise.

[0076] In this embodiment, when W < 1 / 6 inch, the inner diameter D of the central cavity 11 is... g Compared to the outer diameter D of the sleeve 3 o 1 inch larger;

[0077] When 1 / 6 inch ≤ W < 1 / 4 inch, the inner diameter D of the central cavity 11 g Compared to the outer diameter D of the sleeve 3 o Large 6W.

[0078] In this embodiment, when the central cavity 11 needs to be offset, the inner diameter D of the central cavity 11 is... g The plan

[0079] The formula is:

[0080]

[0081] Based on the above-described preferred embodiments of the present invention, and through the foregoing description, those skilled in the art can make various changes and modifications without departing from the inventive concept. The technical scope of this invention is not limited to the contents of the specification, but must be determined according to the scope of the claims.

Claims

1. A surge and blockage prevention angle valve, comprising a valve body (1), a valve cover (2), a valve core (4), and an actuator, wherein the valve body (1) has a central cavity (11) and an inlet flow channel (12) and an outlet flow channel (13) respectively communicating with the central cavity (11) and perpendicular to each other; the valve cover (2) is fitted over the end of the central cavity (11) away from the inlet flow channel (12); characterized in that, It also includes a sleeve (3), which is installed in the middle cavity (11) and coaxially arranged with the inlet channel (12). The sleeve (3) has a small-hole section (31) and a large-hole section (32) along the axial direction. The peripheral wall of the small-hole section (31) is provided with multiple small liquid outlet holes (311), and the peripheral wall of the large-hole section (32) is provided with multiple large liquid outlet holes (321). The small-hole section (31) is closer to the inlet channel (12) than the large-hole section (32). The valve core (4) is slidably installed inside the sleeve (3) and can slide away from the inlet channel (12) to avoid part of the large outlet hole (321); the actuator (5) is connected to the valve core (4) and is used to drive the valve core (4) to move toward the inlet channel (12) to close the inlet channel (12) and to drive the valve core (4) to move away from the inlet channel (12) to open the inlet channel (12). There is a space along the circumference between the outer peripheral wall of the sleeve (3) and the peripheral wall of the middle cavity (11), and the size of the space matches the outflow channel (13); when the valve core is in the open position of the inflow channel (12), the fluid enters the sleeve (3) from the inflow channel (12), then enters the space from the small liquid outlet (311) and the large liquid outlet (321), and finally exits from the outflow channel (13); When W ≥ 1 / 4 inch, the offset dimension o of the peripheral wall of the cavity (11) relative to the outer peripheral wall of the sleeve (3) is = The distance a = 45° angle opposite to the outlet channel (13) between the peripheral wall of the cavity (11) and the outer peripheral wall of the sleeve (3) The distance b = 3 between the peripheral wall of the cavity (11) and the outer peripheral wall of the sleeve (3) at a 45° angle near the outlet channel (13). ; When W < 1 / 4 inch, the offset dimension o of the peripheral wall of the central cavity (11) relative to the outer peripheral wall of the sleeve (3) is 0.0; wherein, In the formula, The inner diameter of the outflow channel (13) is indicated by h; h represents the larger of the valve stroke and the inner diameter of the outflow channel (13).

2. The anti-surge and anti-blockage angle valve according to claim 1, characterized in that, The inner diameter of the inlet channel (12) is smaller than the inner diameter of the outlet channel (13).

3. The anti-surge and anti-blockage angle valve according to claim 1, characterized in that, It also includes a valve seat sealing pair (6), which is installed at the junction of the inlet flow channel (12) and the middle cavity (11), and includes a hard valve seat (61) and a soft valve seat (62). The hard valve seat (61) is installed in the middle cavity (11) and is provided with an insert groove, and the soft valve seat (62) is embedded in the insert groove; wherein, The hard valve seat (61) is used to contact the valve core (4) to achieve a hard seal, and the surface of the hard valve seat (61) that is used to contact the valve core (4) is a conical surface. The soft valve seat (62) is used to contact the valve core (4) to achieve a soft seal. The hard valve seat (61) has a flange (611) extending beyond the soft valve seat (62) toward the central axis of the inlet channel (12).

4. The anti-surge and anti-blockage angle valve according to claim 1, characterized in that, The sleeve (3) has two parts, namely an upper sleeve and a lower sleeve. The upper sleeve and the lower sleeve are axially sealed and spliced ​​together. The small hole section (31) and the large hole section (32) are both provided on the lower sleeve.

5. The anti-surge and anti-blockage angle valve according to claim 1, characterized in that, The diameter of the small outlet hole (311) is 2.99-3.01 mm, and the diameter of the large outlet hole (321) is 4.99-5.01 mm. Alternatively, the diameter of the small outlet hole (311) may be 4.99-5.01 mm, and the diameter of the large outlet hole (321) may be 7.99-8.01 mm.

6. The anti-surge and anti-blockage angle valve according to claim 1, characterized in that, The valve core (4) includes a circumferential side plate (41) and end plates (42) disposed at both ends of the circumferential side plate (41). Each end plate (42) is provided with a balance hole (421) at a non-edge position.

7. The anti-surge and anti-blockage angle valve according to claim 1, characterized in that, The valve core (4) has a limiting pad (43) on its end face facing the valve cover (2) for abutting against the valve cover (2).

8. The anti-surge and anti-blockage angle valve according to claim 1, characterized in that, The valve cover (2) is pressed against the valve body (1) and the sleeve (3) respectively, and a sealing gasket (9) is provided between the valve cover (2) and the valve body (1) and between the valve cover (2) and the sleeve (3).

9. The anti-surge and anti-blockage angle valve according to claim 1, characterized in that, When W < 1 / 6 inch, the inner diameter of the middle cavity (11) Compare the outer diameter of the sleeve (3) 1 inch larger; When 1 / 6 inch ≤ W < 1 / 4 inch, the inner diameter of the cavity (11) Compare the outer diameter of the sleeve (3) Large 6W.

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