Anti-surge and anti-blocking angle valve

Abstract

The invention relates to the field of angle valves, in particular to an anti-surge and anti-blocking angle valve. The angle valve comprises a valve body, a valve cover, a sleeve, a valve element and an executing mechanism. The valve body is provided with a middle cavity, an inflow runner and an outflow runner, the valve cover covers the end part, far away from the inflow runner, of the middle cavity; the sleeve is installed in the middle cavity and coaxially arranged with the inflow runner, the sleeve is provided with a small hole section and a large hole section in the axial direction, a plurality of small liquid outlet holes are formed in the peripheral wall of the small hole section, a plurality of large liquid outlet holes are formed in the peripheral wall of the large hole section, and the small hole section is closer to the inflow runner than the large hole section; the valve element is installed in the sleeve in a sliding mode and can slide back to the inflow runner to avoid part of the large liquid outlet holes. The executing mechanism is connected with the valve element and used for driving the valve element to move towards the inflow runner to close the inflow runner and driving the valve element to move back to the inflow runner to open the inflow runner. Vibration and noise of fluid in the angle valve can be effectively reduced, surge of an applied pipeline is prevented, and vibration reduction, noise reduction and blockage prevention are both considered.

Description

Technical Field

[0001] The invention relates to the field of angle valves, and in particular to an anti-surge and anti-blocking angle valve. Background Art

[0002] A conventional angle valve (angle stop 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 installed on the valve body, and the valve core is slidably installed in the central cavity. The actuator is connected to the valve core. When the valve core is driven to move downward to block the inlet flow channel, the valve is closed. When the valve core is driven to move upward to open the inlet flow channel, the valve is opened, and the fluid enters the central cavity from the inlet channel and then flows out from the outlet channel.

[0003] For example, the patent with application number CN202320468288.X and patent name "Sealing device for angle stop valve" and the patent with application number CN201720996368.7 and patent name "An angle stop valve" both adopt the above structure. In the angle valve with the above structure, the fluid will generate great vibration and noise in the process of flowing from the middle cavity into the outflow channel due to high flow rate and large pressure difference. Angle valves are generally used in pipelines of heat pump compressors, etc., so the vibration and noise of the angle valve will cause the pipeline to surge, thereby affecting the pressure, flow and other characteristics in 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-blocking angle valve, which can effectively reduce the vibration and noise of the fluid in the angle valve, prevent the surge of the applied pipeline, and take into account the vibration and noise reduction and anti-blocking problems.

[0005] In order to solve the above technical problems, the technical solution of the present invention is: an anti-surge and anti-blocking angle valve, comprising a valve body, a valve cover, a valve core and an actuator, the valve body having a central cavity and an inlet flow channel and an outlet flow channel respectively connected to the central cavity and perpendicular to each other; the valve cover is installed at the end of the central cavity away from the inlet flow channel;

[0006] The anti-surge and anti-blocking angle valve also includes a sleeve, which is installed in the middle cavity, coaxially arranged with the inlet flow channel, and has a small hole section and a large hole section along the axial direction, the peripheral wall of the small hole section is provided with a plurality of small liquid outlet holes, the peripheral wall of the large hole section is provided with a plurality of large liquid outlet holes, and the small hole section is closer to the inlet flow channel than the large hole section; wherein,

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

[0008] A space is reserved between the outer wall of the sleeve and the peripheral wall of the middle cavity along the circumferential direction, and the size of the space matches the outlet flow channel; when the valve core is in the state of opening the inlet flow channel, the fluid enters the sleeve from the inlet flow channel, then enters the space from the small outlet hole and the large outlet hole, and is finally discharged from the outlet flow channel.

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

[0010] In order to provide reliable sealing for a long time, the anti-surge and anti-blocking angle valve also includes a valve seat sealing pair, which is installed at the intersection of the inlet flow channel and the middle cavity, including a hard valve seat and a soft valve seat, the hard valve seat is installed in the middle cavity and is provided with an embedding groove, and the soft valve seat is embedded in the embedding groove; wherein,

[0011] The hard valve seat is used to contact with the valve core to achieve hard sealing, and the surface of the hard valve seat used to contact with the valve core is a conical surface, and the soft valve seat is used to contact with the valve core to achieve soft sealing;

[0012] The hard valve seat has a flange that extends beyond the soft valve seat toward the center axis of the inlet flow passage.

[0013] In order 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 sealed and spliced ​​along the axial direction, and the small hole section and the large hole section are both arranged on the lower sleeve.

[0014] In order to further improve the reliability of the seal between the two sleeves, a spring energy storage seal ring is arranged between the upper sleeve and the lower sleeve, and a guide belt for guiding the movement of the valve core is arranged on the inner peripheral wall of at least one sleeve.

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

[0016] Or the aperture of the small liquid outlet hole is 4.99-5.01 mm, and the aperture of the large liquid outlet hole is 7.99-8.01 mm.

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

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

[0019] In order to further achieve the function of internal and external double sealing, the valve cover is crimped with the valve body and the sleeve respectively, and sealing gaskets are respectively arranged between the valve cover and the valve body and between the valve cover and the sleeve.

[0020] In order to maintain a relatively constant flow rate in the valve body to avoid pipeline surge, when W ≥ 1 / 4 inch, the offset size of the central cavity wall compared to the sleeve outer wall is The distance between the central cavity wall and the outer peripheral wall of the sleeve at a 45° angle on the opposite side of the outlet flow channel is a=W, and the distance between the central cavity wall and the outer peripheral wall of the sleeve at a 45° angle close to the outlet flow channel is b=3W;

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

[0022]

[0023] Where D oi It represents the inner diameter of the outlet flow channel; h represents the larger value of the valve stroke and the inner diameter of the outlet flow channel.

[0024] Furthermore, when W is less than 1 / 6 inch, the inner diameter D of the middle cavity is g Ratio of sleeve outer diameter D o 1 inch larger;

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

[0026] After adopting the above technical solution, the present invention sets a liquid outlet hole on the peripheral wall of the sleeve, and changes the beam jet of a large hole into a dispersed jet of multiple small holes, so that the energy of the fluid passing through the liquid outlet hole is gradually consumed, the direction of the fluid is continuously changed, the fluid flow rate is reduced, the pressure is controlled, and the vibration and noise are reduced. The present invention also sets a small liquid outlet hole at the part of the sleeve close to the inlet flow channel, and sets a large liquid outlet hole at a position of the sleeve slightly away from the inlet flow channel. If the impurity particles entering the inlet flow channel block the small liquid outlet hole, they will be pushed out of the large liquid outlet hole above by the flowing fluid, so that the aperture of the small liquid outlet hole is not limited by the size of the impurity particles, and can be made smaller, achieving better vibration and noise reduction effects, and can effectively reduce the vibration and noise of the fluid in the angle valve, thereby preventing the pipeline used by the angle valve from surging, and also solving the problem that vibration and noise reduction and anti-blocking cannot be taken into account at the same time. BRIEF DESCRIPTION OF THE DRAWINGS

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

[0028] Figure 2 It is a cross-sectional view of a sleeve with a large liquid outlet hole and a small liquid outlet hole of the anti-surge and anti-blocking angle valve of the present invention;

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

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

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

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

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

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

[0035] Fig. 9 It is a schematic diagram of the positions of the central cavity peripheral wall and the sleeve peripheral wall when they are offset in the present invention;

[0036] In the figure, 1. valve body; 11. middle cavity; 12. inlet flow channel; 13. outlet flow channel; 2. valve cover; 3. sleeve; 31. small hole section; 311. small outlet hole; 32. large hole section; 321. large 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 belt; 9. sealing gasket; 10. valve stem. DETAILED DESCRIPTION

[0037] In order to make the contents of the present invention more clearly understood, the present invention is further described in detail below based on specific embodiments in conjunction with the accompanying drawings.

[0038] like Figures 1 to 9 As shown, an anti-surge and anti-blocking angle valve comprises a valve body 1, a valve cover 2, a valve core 4 and an actuator, the valve body 1 having a central cavity 11 and an inlet flow channel 12 and an outlet flow channel 13 respectively connected to the central cavity 11 and perpendicular to each other; the valve cover 2 is installed at the end of the central cavity 11 away from the inlet flow channel 12;

[0039] The anti-surge and anti-blocking angle valve also includes a sleeve 3, which is installed in the middle cavity 11, coaxially arranged with the inlet flow channel 12, and has a small hole section 31 and a large hole section 32 along the axial direction, and the peripheral wall of the small hole section 31 is provided with a plurality of small liquid outlet holes 311, and the peripheral wall of the large hole section 32 is provided with a plurality of large liquid outlet holes 321, and the small hole section 31 is closer to the inlet flow channel 12 than the large hole section 32; wherein,

[0040] The valve core 4 is slidably installed in the sleeve 3, and can slide away from the inlet flow channel 12 to avoid part of the large liquid 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 flow channel 12 to close the inlet flow channel 12 and drive the valve core 4 to move away from the inlet flow channel 12 to open the inlet flow channel 12;

[0041] A space is reserved between the outer wall of the sleeve 3 and the peripheral wall of the middle cavity 11 along the circumferential direction, and the size of the space matches the outlet flow channel 13; when the valve core is in the state of opening 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 is finally discharged from the outlet flow channel 13.

[0042] Specifically, a liquid outlet hole is arranged on the peripheral wall of the sleeve 3, and the bundled jet of a large hole is changed into a dispersed jet of multiple small holes, so that the energy of the fluid passing through the valve cage is gradually consumed, the direction of the fluid is continuously changed, the flow rate of the fluid is reduced, the pressure is controlled, and the noise is reduced.

[0043] In addition, considering that the smaller the diameter of the liquid outlet hole, the better the vibration and noise reduction effect, the size of the liquid outlet hole is determined by the required noise level and the size of the impurity particles in the pipeline. If the liquid outlet hole is made smaller, although it can achieve a better vibration and noise reduction effect, it will cause the liquid outlet hole to be blocked. If the aperture of the liquid outlet hole is made larger, although it will not be blocked, it will cause the vibration and noise reduction effect to deteriorate. In other words, the particle size of the impurity particles limits the aperture of the liquid outlet hole, and it is impossible to take into account both the vibration and noise reduction and the anti-blocking problem. Based on this, in this embodiment, a small liquid outlet hole 311 is set at the part of the sleeve 3 close to the inlet flow channel 12, and a large liquid outlet hole 321 is set at a position of the sleeve 3 slightly away from the inlet flow channel 12. If the impurity particles entering the inlet flow channel 12 block the small liquid outlet hole 311, they will be pushed out of the large liquid outlet hole 321 above by the flowing fluid, so that the aperture of the small liquid outlet hole 311 is not limited by the size of the impurity particles, and can be made smaller, thereby achieving better vibration and noise reduction effects, and can effectively reduce the vibration and noise of the fluid in the angle valve, thereby preventing the heat pump compressor used in the angle valve from surging, and also solving the problem that vibration and noise reduction and anti-blocking cannot be taken into account at the same time.

[0044] It should be noted that if there is a higher noise reduction requirement, a stepped hole sleeve, a double-layer sleeve, etc. can also be designed. The aperture of the large liquid outlet 321 is determined according to the particle size of the impurity particles that need to pass through. The fluid entering the inlet flow channel 12 is filtered through the front end and will not have too large impurities.

[0045] In this embodiment, if Figure 8 As shown, the valve cover 2 is in a spherical can shape, which can better withstand pressure and distribute the pressure more evenly to the valve cover 2 shell. Compared with the flat valve cover, the spherical can-shaped valve cover 2 has better force and pressure bearing performance. The spherical can-shaped valve cover 2 can also make the volume in the valve cavity larger, provide a larger stroke for the valve, and reduce the volume and weight of the valve.

[0046] In this embodiment, if Figure 1 and Figure 6 As shown, the actuator 5 is connected to the valve core 4 through the valve stem 10. The valve stem 10 and the valve body 1 are filled with packing and compressed by the disc spring, so as to provide lasting pressure, prevent leakage and reduce maintenance costs. The disc spring bears static or dynamic loads acting in the axial direction at the upper inner edge and the lower outer edge, and is deformed after being compressed until it is flattened, and stores energy as a live load, which is automatically converted into the additional compression load required for sealing when necessary, so as to reduce the continuous requirements for compression of the packing during use, and reduce unnecessary downtime and maintenance time and leakage losses. After the disc spring is deformed under the load, it stores a certain amount of potential energy. When the bolts connecting the valve cover 2 and the disc spring and packing are loose, the disc spring releases part of the potential energy to maintain the pressure to meet the sealing requirements. The stress distribution of the disc spring decreases evenly from the inside to the outside, which can achieve the effect of low stroke and high compensation force.

[0047] In one embodiment, Figure 1 As shown, the inner diameter of the inlet flow channel 12 is smaller than the inner diameter of the outlet flow channel 13. In this way, the valve noise can be further reduced.

[0048] In one embodiment, Figure 1 and Figure 4 As shown, the anti-surge and anti-blocking angle valve also includes a valve seat sealing pair 6, which is installed at the intersection 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 embedding groove, and the soft valve seat 62 is embedded in the embedding groove; wherein,

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

[0050] The hard valve seat 61 has a flange 611 that extends beyond the soft valve seat 62 toward the center axis of the inlet flow passage 12 .

[0051] Specifically, the material of the soft valve seat 62 has a certain elasticity, and the processing accuracy requirements are lower than those of the hard valve seat 61, and the sealing performance is better. An O-ring 63 is also provided between the soft valve seat 62 and the hard valve seat 61. The O-ring 63 and the soft valve seat 62 are integrally embedded in the hard valve seat 61, and the hard valve seat 61 can be a metal valve seat. In this embodiment, the valve seat sealing pair 6 adopts a double sealing design of a hard valve seat 61 seal and a soft valve seat 62 seal. The hard valve seat 61 can play a supporting role to prevent the soft valve seat 62 from being crushed due to excessive pressure. The soft valve seat 62 is supported by an elastic O-ring and protected by the hard valve seat 61. The hard valve seat 61 can also avoid the danger of overloading the soft valve seat 62, so that the valve achieves an excellent sealing effect and a longer service life. When the valve is fully closed, the hard valve seat 61 seals and the soft valve seat 62 act simultaneously, and the seal is tight and reliable; when the valve is fully open, the soft valve seat 62 recovers its elasticity.

[0052] Moreover, generally, at the moment when the valve is just opened, the medium generates a rapid turbulence at the outer edge of the seal, which will cause the seal to vibrate and fatigue the seal material. In this embodiment, the hard valve seat 61 has a flange 611 that extends beyond the soft valve seat 62 toward the central axis of the inlet flow channel 12. Due to the protection of the flange 611, the soft valve seat 62 will not be washed by the fluid and is not easily damaged.

[0053] In addition, for fluid media with solid particles, the valve seat sealing structure is more important. This is mainly because when solid particles are entrained in the medium, they are easily stuck between the valve core 2 and the sealing surface of the valve seat, hindering the sealing of the valve seat and causing leakage. Then, due to the high-speed erosion of the medium, the surface of the valve seat is eroded and damaged. In this embodiment, even if such particles are stuck between the valve core 4 and the hard valve seat 61, there will be no harm, because there is still a seal between the valve core 4 and the soft valve seat 61, which can still play a reliable and effective supplementary sealing role.

[0054] In one embodiment, Figure 1 and Figure 5 As shown, the sleeve 3 has two sleeves, an upper sleeve and a lower sleeve, the upper sleeve and the lower sleeve are sealed and spliced ​​along the axial direction, and the small hole section 31 and the large hole section 32 are both arranged on the lower sleeve.

[0055] In this way, the length of a single sleeve 3 can be reduced, making it easier to process, and large-hole operations can also be better performed on a relatively short sleeve 3.

[0056] In one embodiment, Figure 1 and Figure 5 As shown, a spring energy storage seal ring 7 is arranged between the two sleeves 3, wherein the inner peripheral wall of at least one sleeve 3 is provided with a guide belt 8 for guiding the movement of the valve core 4.

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

[0058] Or the aperture of the small liquid outlet hole 311 is 4.99-5.01 mm, and the aperture of the large liquid outlet hole 321 is 7.99-8.01 mm.

[0059] It should be noted that the aperture of the small liquid outlet hole 311 is determined according to the noise reduction requirement, and the aperture of the large liquid outlet hole 321 is determined according to the size of the impurity particles.

[0060] For spring energized seals 7, when the seal is installed in the sealing groove, the spring is compressed, causing the jacket lip to fit tightly against the sealing groove, thereby forming a seal. The spring provides permanent elastic force to the sealing jacket and compensates for material wear and offset or eccentricity of mating parts. System pressure valve inlet and outlet pressure also assists in energizing the sealing jacket. The spring force assisted by the system pressure can achieve effective sealing at both high and low pressures. The geometry of the seal installed in the sealing groove also avoids the twisting or spiral failure problems common to O-rings. Under pressure, the PTFE material in the seal tends to flow into the bite gap. Dynamic reciprocating motion increases bite. Under static conditions, when the pressure, temperature and bite gap are below certain limits, the bite will stop once the pressure generated by the friction in the bite gap equals the system pressure.

[0061] As for the guide belt 8, the guide belt 8 plays the role of preventing the valve core 4 and the sleeve 3 from wearing and protecting the spring energy storage seal ring 7. It has good heat resistance, corrosion resistance, and friction resistance guiding characteristics, and can absorb radial changes in vibration performance at any time. The guide belt has the following advantages: small conflict force; good dustproof effect; can compensate for gap force; wear resistance and long life; can withstand mechanical vibration; avoid contact between metals; can absorb lateral loads; the guide belt 8 has a centering effect, which can increase the extrusion gap of the seal.

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

[0063] The valve core 4 of this structure is a hollow structure, which can reduce the weight of the entire angle valve. In addition, a balancing hole 421 is provided on the end plate 42 to make the pressure inside the valve core 4 and the pressure at the inlet flow channel 12 equal, thereby preventing the valve core 4 from being deformed by pressure and also preventing the inner side of the valve core 4 from being directly impacted by the fluid.

[0064] In one embodiment, Figure 1 and Figure 6As shown, the end surface 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 the valve core 4 , if the limit switch of the actuator 5 fails, the limit pad 43 directly abuts against the valve cover 2 , acting as a buffer zone to protect the valve core 4 and the root of the valve stem 10 .

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

[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 the valve cover 2 and the sleeve 3, and between the sleeve 3 and the valve body 1, which have a good effect on the alignment and non-displacement of parts during assembly. There is also a gap design between the sleeve 3 and the valve cover 2, which can effectively avoid the phenomenon of inconsistent thermal expansion and deformation of the pressure-bearing parts such as the valve cover 2 and the valve body 1 and the valve internal parts such as the sleeve 3 when the valve expands and contracts due to heat, and radial dimension compensation is performed for possible thermal expansion and deformation. During the assembly of the valve, it is best to fully compress the gasket to minimize the misalignment between the sliding parts. The compression load of the spirally wound gasket is the smallest, which is higher than the load required for sealing and the rebound force on the seal. The bolt load and gasket load need to be calculated according to the standard formula.

[0069] In one embodiment, when W ≥ 1 / 4 inch, the offset dimension of the peripheral wall of the middle cavity 11 compared to the peripheral wall of the sleeve 3 is The distance a between the peripheral wall of the middle cavity 11 and the outer peripheral wall of the sleeve 3 at a 45° angle on the opposite side of the outlet flow channel 13 is W, and the distance b between the peripheral wall of the middle cavity 11 and the outer peripheral wall of the sleeve 3 at a 45° angle close to the outlet flow channel 13 is 3W. Fig. 9 As shown;

[0070] When W is less than 1 / 4 inch, the offset dimension o of the peripheral wall of the middle cavity 11 compared to the peripheral wall of the sleeve 3 is 0.0; wherein,

[0071]

[0072] Where D oi represents the inner diameter of the outlet flow channel 13; h represents the larger value of the valve stroke and the inner diameter of the outlet flow channel 13.

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

[0074] Specifically, if the size formed by the middle cavity 11 and the sleeve 3 is not appropriate and does not match the outlet flow channel 13, the valve will have a higher flow resistance and does not meet the valve Cv flow coefficient, thereby causing noise and vibration problems. By calculating with the formula in this embodiment, it can be ensured that the size of the middle cavity 11 matches the outlet flow channel 13, and a relatively constant flow rate is maintained in the valve body 1, thereby reducing noise and vibration, and further avoiding pipeline surge.

[0075] The design of the center cavity 11 of the valve body 1 can be concentric or eccentric. The eccentric design of the center cavity 11 will make the diameter of the center cavity 11 smaller, thereby reducing the size of the valve body casting, but still maintaining the flow rate. The wall thickness and flow channel diameter will become smaller as the center cavity 11 is offset, and the thickness of the top and bottom of the valve body 1 will also be affected. For flow channels with smaller diameters, the thickness of the top and bottom of the valve body 1 will become thinner. This eccentric design of the center cavity 11 is easy to achieve in casting, but requires additional machining settings in forging structures. Smaller-sized valves usually use a concentric center cavity design because the cost savings may be minimal. The eccentric center cavity 11 is generally used in large-sized valves and is cast. In addition, the eccentric center cavity 11 can design the largest possible Cv flow coefficient with the smallest possible volume. In addition, the eccentric center cavity 11 allows most of the center cavity 11 to be located in the outlet flow channel 13, which can also further reduce noise.

[0076] In this embodiment, when W is less than 1 / 6 inch, the inner diameter D of the middle cavity 11 is g Than the outer diameter D of sleeve 3 o 1 inch larger;

[0077] When 1 / 6 inch ≤ W < 1 / 4 inch, the inner diameter D of the middle cavity 11 g Than the outer diameter D of sleeve 3 o Big 6W.

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

[0079] The calculation formula is:

[0080]

[0081] Based on the above ideal embodiments of the present invention, the relevant staff can make various changes and modifications without departing from the technical concept of the present invention through the above description. The technical scope of the present invention is not limited to the contents of the specification, and its technical scope must be determined according to the scope of the claims.

Claims

1. An anti-surge and anti-blocking 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 connected to the central cavity (11) and perpendicular to each other; the valve cover (2) is mounted on the end of the central cavity (11) away from the inlet flow channel (12); and ... outlet flow channel (13) respectively connected to the central cavity (11) and perpendicular to each other; and the valve cover (2) is mounted on the end of the central cavity (11) away from the inlet flow channel (12); and the valve body (1) has a central cavity (11) and an outlet flow channel (13) respectively connected to the central cavity (11) and perpendicular to each other; and the valve cover (2) is mounted on the central cavity (11) and an end of the central cavity (11) away from the inlet flow channel (12); and the valve body (1) has a central cavity (11) and an outlet flow channel (13) respectively connected to the central cavity (11) and perpendicular to each other; and the valve cover (2) is mounted on the central cavity (11) and an outlet flow channel (13) It also comprises a sleeve (3), the sleeve (3) being installed in the middle cavity (11), being coaxially arranged with the inlet flow channel (12), and having a small hole section (31) and a large hole section (32) along the axial direction, the peripheral wall of the small hole section (31) being provided with a plurality of small liquid outlet holes (311), the peripheral wall of the large hole section (32) being provided with a plurality of large liquid outlet holes (321), the small hole section (31) being closer to the inlet flow channel (12) than the large hole section (32); wherein, The valve core (4) is slidably mounted in the sleeve (3), and is capable of sliding away from the inlet flow channel (12) to avoid a portion of the large liquid 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 flow channel (12) to close the inlet flow channel (12) and to drive the valve core (4) to move away from the inlet flow channel (12) to open the inlet flow channel (12); A space is reserved between the outer wall of the sleeve (3) and the peripheral wall of the middle cavity (11) along the circumferential direction, and the size of the space matches the outlet flow channel (13); when the valve core is in the state of opening 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 is discharged from the outlet flow channel (13).

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

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

4. The anti-surge and anti-blocking angle valve according to claim 1, characterized in that: The sleeve (3) has two sleeves, namely an upper sleeve and a lower sleeve. The upper sleeve and the lower sleeve are sealed and spliced ​​along the axial direction. The small hole section (31) and the large hole section (32) are both arranged on the lower sleeve.

5. The anti-surge and anti-blocking angle valve according to claim 1 is characterized in that: The aperture of the small liquid outlet hole (311) is 2.99-3.01 mm, and the aperture of the large liquid outlet hole (321) is 4.99-5.01 mm; Or the aperture of the small liquid outlet hole (311) is 4.99-5.01 mm, and the aperture of the large liquid outlet hole (321) is 7.99-8.01 mm.

6. The anti-kick and anti-blocking angle valve according to claim 1, characterized in that: The valve core (4) comprises a circumferential side plate (41) and end plates (42) arranged at both ends of the circumferential side plate (41), and each end plate (42) is provided with a balancing hole (421) at a non-edge position.

7. The anti-surge and anti-blocking angle valve according to claim 1, characterized in that: The end surface of the valve core (4) facing the valve cover (2) is provided with a limiting cushion block (43) for abutting against the valve cover (2).

8. The anti-surge and anti-blocking angle valve according to claim 1, characterized in that: The valve cover (2) is respectively pressed against the valve body (1) and the sleeve (3), and sealing gaskets (9) are respectively 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-blocking angle valve according to claim 1, characterized in that: In the case where W is greater than or equal to 1 / 4 inch, the offset dimension of the peripheral wall of the middle cavity (11) compared to the peripheral wall of the sleeve (3) is The distance a between the peripheral wall of the middle cavity (11) and the outer peripheral wall of the sleeve (3) at a 45° angle on the opposite side of the outlet flow channel (13) is W, and the distance b between the peripheral wall of the middle cavity (11) and the outer peripheral wall of the sleeve (3) at a 45° angle on the side close to the outlet flow channel (13) is 3W; When W is less than 1 / 4 inch, the offset dimension o of the peripheral wall of the middle cavity (11) compared to the peripheral wall of the sleeve (3) is 0.0; wherein, Where D oi represents the inner diameter of the outlet flow channel (13); and h represents the larger value of the valve stroke and the inner diameter of the outlet flow channel (13).

10. The anti-surge and anti-blocking angle valve according to claim 9, characterized in that: When W is less than 1 / 6 inch, the inner diameter D of the middle cavity (11) is g The outer diameter D of the sleeve (3) o 1 inch larger; When 1 / 6 inch ≤ W < 1 / 4 inch, the inner diameter D of the middle cavity (11) is g The outer diameter D of the sleeve (3) o Big 6W.

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