A wear-resistant double-gate multi-channel fluid distribution gate valve

Abstract

This invention relates to the field of fluid distribution technology and discloses a wear-resistant double-gate multi-channel fluid distribution gate valve. It includes a fluid distribution structure, with a fluid pipeline comprising, along the fluid direction, a first pipe, a second pipe, a third pipe, and an outlet channel connected sequentially. The first and third pipes are two-way pipes, each equipped with a front gate valve and a rear gate valve, respectively. The second pipe and the outlet channel are three-way pipes, and the second pipe is also connected to a fourth pipe, the end of which is connected to the outlet channel. A throttling mechanism is installed within the fourth pipe. When the front gate valve is open and the rear gate valve is closed, the fluid distribution structure provides a continuous small flow rate. When both the front and rear gate valves are open, the fluid distribution structure provides a continuous large flow rate. This invention solves the problems of traditional gate valves, which, due to structural limitations, can only be fully open or fully closed and cannot participate in flow regulation, as well as the high wear and short lifespan caused by the erosion of the sealing surface by high-speed media during opening and closing.

Description

Technical Field

[0001] This invention relates to the field of fluid distribution technology, specifically to a wear-resistant double-gate multi-channel fluid distribution gate valve. Background Technology

[0002] Gate valves, as a common type of shut-off valve, are widely used in pipeline systems such as petroleum, chemical, natural gas, urban water supply, and gas pipelines due to their advantages such as simple structure, low flow resistance, and reliable sealing performance. Their opening and closing element is a gate, which achieves full opening or full closing through linear movement perpendicular to the fluid direction. However, gate valves were originally designed primarily for shut-off applications, not flow regulation. According to the American Petroleum Institute (API 600) standard and relevant chapters in the *Valve Engineering Handbook*, the flow characteristic curve of a gate valve exhibits strong nonlinearity when partially open. When the opening is less than 30%, the flow velocity increases sharply, easily leading to problems such as cavitation, sealing surface erosion, and pipeline vibration. Therefore, in engineering practice, the use of gate valves for flow regulation scenarios is generally not recommended.

[0003] In existing technologies, when gate valves are operated at high frequencies or in a partially open state for extended periods, their sealing surfaces are easily worn down by the scouring effect of high-speed media, leading to decreased sealing performance and shortened service life. For example, studies have shown that the sealing surface life of gate valves operating at 50% opening for extended periods is reduced by approximately 60% compared to the fully open state. Furthermore, during the opening and closing process, especially under high pressure differential or particulate media conditions, the sealing surfaces of gate valves are highly susceptible to impact and scratches, further exacerbating equipment wear.

[0004] To address the aforementioned issues, some improvements have been implemented in existing technologies. For example, a double-gate structure combined with spring elastic support can improve the fit of the sealing surface and compensate for machining angle deviations. Another approach involves a variable flow channel design, incorporating pressure-reducing and pressure-distributing components to optimize fluid flow and reduce the impact force on the valve disc during opening and closing. However, these solutions primarily focus on optimizing the internal structure of the gate valve and fail to fundamentally solve the problem of gate valves' inability to participate in flow regulation. Furthermore, high losses during the opening and closing process remain difficult to avoid in practical applications.

[0005] Furthermore, some existing technologies have attempted to combine gate valves with throttling elements, such as installing throttling valves or regulating valves in parallel in pipelines to achieve segmented flow control. However, this approach typically requires additional valves or fittings in the main process, leading to a complex system structure, increased costs, and inconvenient maintenance. More importantly, existing solutions still struggle to prevent direct wear of the main valve sealing surface under high pressure differentials or high-speed fluid impacts when switching operating modes.

[0006] In summary, the main technical bottlenecks in the application of existing gate valves are: firstly, gate valves themselves lack flow regulation capabilities, failing to meet the demands of operating conditions requiring switching between large and small flow rates; secondly, the high losses of gate valves during opening, closing, or partial opening have not been effectively resolved, especially under conditions of frequent switching or particulate media, resulting in a significant decrease in the lifespan of the sealing surface. Therefore, there is an urgent need for a technical solution that can maintain the inherent advantages of gate valves (such as low flow resistance and high sealing performance), achieve flow regulation functions, and effectively reduce valve losses during opening and closing. Summary of the Invention

[0007] (a) Technical problems to be solved To address the shortcomings of existing technologies, this invention provides a wear-resistant double-gate multi-channel fluid distribution gate valve. Without altering the inherent advantages of gate valves—low flow resistance and high sealing performance—it achieves stable switching between high and low flow rates. Simultaneously, it comprehensively reduces the opening and closing losses of the downstream gate valve and provides an independently replaceable throttling module for easy maintenance and flow adjustment. This solves the problems of traditional gate valves, which, due to structural limitations, can only be fully open or fully closed and cannot participate in flow regulation, as well as the high wear and short lifespan caused by the sealing surface being easily eroded by high-speed media during opening and closing.

[0008] (II) Technical Solution To achieve the above objectives, the present invention provides the following technical solution: A wear-resistant double-gate multi-channel fluid distribution valve includes a fluid distribution structure, which includes a fluid pipeline. The fluid pipeline includes a first pipeline, a second pipeline, a third pipeline, and a water outlet channel connected sequentially along the fluid direction. Pipeline 1 and Pipeline 3 are two-way pipes and are each equipped with a front gate valve and a rear gate valve respectively. Pipeline 2 and the water outlet channel are three-way pipes. Pipeline 2 is also connected to Pipeline 4. The end of Pipeline 4 is connected to the water outlet channel. Pipeline 4 is equipped with a throttling mechanism. When both the current gate valve and the rear gate valve are closed, no fluid passes through the fluid distribution structure. When the current gate valve is open and the rear gate valve is closed, the fluid passes through the No. 4 pipe equipped with a throttling mechanism, and the fluid distribution structure provides a continuous flow of small volume. When both the current gate valve and the rear gate valve are open, the fluid passes through the No. 3 and No. 4 pipes and flows into the outlet channel, and the fluid distribution structure provides a continuous flow of large volume.

[0009] Preferably, the throttling mechanism includes a ring seat and a throttling orifice plate fixed on the ring seat, with a through hole at the center of the throttling orifice plate, and the ring seat is fixed to the flange at the end of the fourth pipe.

[0010] Preferably, the throttling mechanism includes a throttling orifice plate that can move axially within the fourth pipe for adjusting the fluid state during mode switching.

[0011] Preferably, the fourth pipe includes: A throttling mechanism, comprising a ring seat and a throttling orifice plate fixed on the ring seat, wherein the ring seat is slidably disposed within pipe No. 4; A drive mechanism is used to drive the throttling mechanism to slide within pipe number four. Specifically, before the rear gate valve opens, the throttling mechanism is moved backward by the drive mechanism, so that the high-pressure zone generated in front of the orifice plate is away from the inlet of pipe No. 3; after the rear gate valve opens, the throttling mechanism is moved forward by the drive mechanism, so that the high-speed water flow zone generated behind the orifice plate is away from the outlet of pipe No. 3.

[0012] Preferably, a throttling mechanism is provided inside the fourth pipe, the throttling mechanism comprising: The orifice plate assembly is fixed at the end of pipe number four. A sliding orifice plate assembly is movably connected to the front side of a fixed orifice plate assembly, and the sliding orifice plate assembly and the fixed orifice plate assembly are connected by an elastic component. The orifice diameter of the throttling orifice plate on the sliding orifice plate assembly is larger than that on the fixed orifice plate assembly. The pressure difference inside the pipe acts on the sliding orifice plate assembly, enabling the sliding orifice plate assembly to slide adaptively within pipe No. 4.

[0013] Preferably, the fourth pipe includes a central pipe located in the middle and side pipes at both ends of the central pipe, wherein the inner diameter of the central pipe is larger than the inner diameter of the side pipes, and the driving mechanism includes: An external driver is located on the outside of one of the side tubes and is used to drive the lead screw to rotate. A lead screw is installed inside the middle tube. Both ends of the lead screw pass through the end caps at both ends of the middle tube, and the middle position of the lead screw passes through the threaded hole of the ring seat and is threadedly engaged. The guide rod is installed inside the middle tube, with both ends of the guide rod passing through the end caps at both ends of the middle tube, and the middle position of the lead screw passing through the through hole of the ring seat; The lead screw is connected to the external driver at one end, and is driven to rotate by the external driver. The other end of the lead screw is provided with an end cap outside the middle tube for rotating and supporting the lead screw. The guide rod is also provided with end caps outside the middle tube at both ends for rotating and supporting the guide rod.

[0014] Preferably, the outer side of the ring seat is provided with a groove, and a sealing ring is provided in the groove.

[0015] Preferably, the elastic component is a compression spring, installed between the fixed orifice plate assembly and the sliding orifice plate assembly.

[0016] Preferably, the fixed perforated plate assembly and the sliding perforated plate assembly are respectively provided with annular spring seat grooves on their opposite end faces, and the two ends of the spring are respectively embedded in the spring seat grooves.

[0017] A control method for a wear-resistant double-gate multi-channel fluid distribution gate valve includes the following control logic: When the system is in a fully closed state, the front gate valve is closed and the rear gate valve is open; When switching from the fully closed state to the low flow mode, the first operation sequence is as follows: first close the rear gate valve, then open the front gate valve; When switching from low flow mode to high flow mode, the second operation sequence is executed: with the front gate valve kept open, the rear gate valve is opened; When switching from the fully closed state to the high flow mode, the third operation sequence is executed: while the rear gate valve remains open, the front gate valve is opened.

[0018] (III) Beneficial Effects Compared with the prior art, the present invention provides a wear-resistant double-gate multi-channel fluid distribution gate valve, which has the following beneficial effects: 1. This wear-resistant double-gate multi-channel fluid distribution gate valve, through the combined operation of a front gate valve and a rear gate valve, combined with a parallel throttling pipeline, enables the switching between high-flow and low-flow operating modes within the same fluid channel using a gate valve that is only used as a shut-off valve. This expands the application range of the gate valve, allowing it to participate in flow distribution control while maintaining its inherent advantages of low flow resistance and high sealing performance. Furthermore, this improvement also reduces the wear and tear on the rear gate valve, alleviating the problem of increased maintenance costs caused by double gate valves.

[0019] 2. This wear-resistant double-gate multi-channel fluid distribution gate valve, in the fully closed state, has the front gate valve closed and the rear gate valve open, preventing the rear gate valve's sealing surface from contacting the high-speed flowing medium and avoiding direct erosion. When switching from the fully closed state to the low-flow mode, the rear gate valve closes first and then the front gate valve opens, preventing the rear gate valve's sealing surface from being directly impacted and severely worn by the high-velocity medium at the moment of closure. Simultaneously, the throttling mechanism also prevents erosion caused by excessive pressure difference before and after the front gate valve's opening process. When switching from the low-flow mode to the fully open state, the parallel connection between pipeline number four and the channel containing the rear gate valve reduces the pressure difference before and after the rear gate valve, thus comprehensively reducing the wear on the rear gate valve. Switching from the fully open state to the fully closed state or vice versa, a transition through the intermediate low-flow mode is possible, avoiding wear on the gate valve and reducing the maintenance cost of the double gate valve.

[0020] 3. The wear-resistant double-gate multi-channel fluid distribution gate valve has a throttling mechanism installed on an independent No. 4 pipeline, which can be disassembled and replaced separately. If it is necessary to adjust the flow rate, only a throttling mechanism with a different orifice diameter needs to be replaced, without modifying any main pipeline or main valve.

[0021] 4. This wear-resistant double-gate multi-channel fluid distribution gate valve, by setting the throttling mechanism to slide freely within the No. 4 pipe, allows for easy installation of the throttling orifice plate in the middle of the pipe. When a small flow continuously passes through the throttling orifice plate, it can prevent excessive pressure on both sides of the orifice plate from causing leakage at the pipe connection. On the other hand, when switching between the small flow and fully open modes before and after the rear gate valve opens, by controlling the position of the throttling orifice plate, it can reduce the pressure difference between the front and rear sides of the rear gate valve when it is opened, and prevent excessive water flow impact at the confluence of the No. 4 and No. 3 pipes after opening.

[0022] 5. This wear-resistant double-gate multi-channel fluid distribution gate valve, by setting up a fixed orifice plate assembly and a sliding orifice plate assembly, allows for convenient installation of the throttling orifice plate in the middle of the pipeline without using a drive mechanism. On the other hand, the two throttling orifice plates, one large and one small, can form a gradient throttling effect, avoiding excessive throttling intensity at one time, which would cause the throttling orifice plate to wear out quickly. Finally, the elastic connection between the sliding orifice plate assembly and the fixed orifice plate assembly not only facilitates installation but also has the effect of adaptively adjusting the throttling intensity. Attached Figure Description

[0023] Figure 1 This is a schematic diagram of the overall structure of Embodiment 1 and Embodiment 3 of the present invention.

[0024] Figure 2 This is a cross-sectional view of Embodiment 1 of the present invention.

[0025] Figure 3 This is an exploded view of pipe No. 4, throttling mechanism, and water outlet channel in Embodiment 1 of the present invention.

[0026] Figure 4 This is a schematic diagram of the throttling mechanism according to Embodiment 1 of the present invention.

[0027] Figure 5 This is a schematic diagram of the overall structure of Embodiment 2 of the present invention.

[0028] Figure 6 This is a cross-sectional view of Embodiment 2 of the present invention.

[0029] Figure 7 This is a schematic diagram of the structure of pipe No. 4 in Embodiment 2 of the present invention.

[0030] Figure 8 This is an exploded view of the fourth pipe, the throttling mechanism, and the driving mechanism in Embodiment 2 of the present invention.

[0031] Figure 9 This is a schematic diagram of the throttling mechanism according to Embodiment 2 of the present invention.

[0032] Figure 10 This is a cross-sectional view of Embodiment 3 of the present invention.

[0033] Figure 11 This is a half-sectional perspective view of the fourth pipe and the throttling mechanism in Embodiment 3 of the present invention.

[0034] In the diagram: 1. Pipeline 1; 2. Pipeline 2; 3. Pipeline 3; 4. Pipeline 4; 5. Front gate valve; 6. Rear gate valve; 9. Outlet channel; 41. Middle pipe; 42. Side pipe; 7. Throttling mechanism; 71. Throttling orifice plate; 72. Ring seat; 73. Sealing ring; 701. Fixed orifice plate assembly; 702. Sliding orifice plate assembly; 703. Elastic component; 8. Drive mechanism; 81. Lead screw; 82. Guide rod; 83. External driver; 84. End cap. Detailed Implementation

[0035] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0036] In the description of this invention, it should be understood that the terms "length", "width", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are 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.

[0037] In addition, a fixed connection refers to a connection in which parts or components are fixed and there is no relative movement; a transmission connection refers to a connection in which mechanical motion or torque is transmitted to other working parts through a transmission component; a sliding connection refers to a connection in which two objects are in contact but not fixed and can slide relative to each other; and a rotational connection refers to a connection in which two objects are in contact but not fixed and can rotate relative to each other.

[0038] 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 one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0039] Example 1: Existing gate valves can only be fully opened or fully closed, making them unsuitable for applications involving flow regulation. Furthermore, the high losses during opening and closing significantly impact the lifespan of gate valves.

[0040] To address the aforementioned issues, this embodiment provides a wear-resistant double-gate multi-channel fluid distribution gate valve, which has the following technical features.

[0041] Please see Figures 1-4 It includes a fluid distribution structure, which includes fluid pipes, and the fluid pipes include a first pipe 1, a second pipe 2, a third pipe 3 and a water outlet channel 9 connected in sequence along the fluid direction; Pipeline 1 and Pipeline 3 are two-way pipes and are each equipped with a front gate valve 5 and a rear gate valve 6 respectively. Pipeline 2 and water outlet channel 9 are three-way pipes. Pipeline 2 is also connected to Pipeline 4. The end of Pipeline 4 is connected to water outlet channel 9. A throttling mechanism 7 is installed inside Pipeline 4. When both the current gate valve 5 and the rear gate valve 6 are closed, no fluid passes through the fluid distribution structure. When the current gate valve 5 is open and the rear gate valve 6 is closed, fluid passes through the fourth pipe 4, which is equipped with a throttling mechanism 7, and the fluid distribution structure provides a continuous flow of small volume. When both the current gate valve 5 and the rear gate valve 6 are open, fluid passes through the third pipe 3 and the fourth pipe 4 and flows into the outlet channel 9, and the fluid distribution structure provides a continuous flow of large volume.

[0042] It should be noted that this fluid distribution structure is suitable for operating conditions where the upstream inflow pressure is relatively stable and the downstream outlet back pressure fluctuation is small.

[0043] In this embodiment, as Figure 4 As shown, the throttling mechanism 7 includes a ring seat 72 and a throttling orifice plate 71 fixed on the ring seat 72. A through hole is provided at the center of the throttling orifice plate 71, and the ring seat 72 is fixed on the end flange of the fourth pipe 4.

[0044] It should be noted that this invention is not applicable to occasions requiring frequent and rapid opening and closing or where there is severe water hammer impact.

[0045] It should be noted that the fluid flow path and pressure distribution principle in low-flow mode are as follows: In low-flow mode, the front gate valve 5 is open and the rear gate valve 6 is closed. Fluid flows in from pipe 1, passes through pipe 2, and then enters pipe 4. Since the end of pipe 4 is directly connected to the outlet channel 9, and pipe 3 is closed due to the closure of the rear gate valve 6, the fluid can only flow out through the orifice plate 71 in pipe 4. The central through-hole of the orifice plate 71 creates local resistance. When the fluid passes through the through-hole, the flow velocity increases and the pressure decreases, generating a stable pressure difference before and after the orifice plate. This pressure difference follows a square root relationship with the flow rate. Where Q is the volumetric flow rate through the orifice plate, ΔP is the pressure difference across the orifice plate, and K is a coefficient related to the orifice plate geometry and fluid properties. Since the orifice diameter of the orifice plate 71 is calculated based on the maximum allowable minimum flow rate and the maximum possible pressure difference, it can provide a continuous and stable flow output in low flow rate mode.

[0046] It should be noted that the confluence mechanism in high-flow mode is as follows: In high-flow mode, both the front gate valve 5 and the rear gate valve 6 are open. After the fluid flows in from pipe 1, it splits into two paths at pipe 2: one path flows directly to the outlet channel 9 via pipe 3; the other path flows to the outlet channel 9 via pipe 4 through the orifice plate 71. The two streams merge in the outlet channel 9 and are then discharged. Because the flow area of ​​pipe 3 is much larger than the orifice plate 71 of pipe 4, most of the fluid flows through pipe 3, and a small portion flows through pipe 4. When the rear gate valve 6 is fully open, its gate is completely retracted into the valve cover and not exposed in the flow channel; therefore, the flow resistance is minimal and does not affect the high-flow rate.

[0047] It should be noted that the mechanism by which the gate valve operation sequence protects the sealing surface is as follows: When switching from a fully closed state to a low-flow mode, the operation sequence of closing the rear gate valve 6 first and then opening the front gate valve 5 plays a crucial protective role. In the fully closed state, the front gate valve 5 is closed and the rear gate valve 6 is open, with no fluid flowing within the system. When the rear gate valve 6 is closed first, since the front gate valve 5 is still closed, there is no pressure difference or a very small pressure difference across the rear gate valve 6 (only generated by the static pressure of the residual fluid in the pipeline). Therefore, the sealing surface of the rear gate valve 6 experiences almost no wear during the closing process. Subsequently, when the front gate valve 5 is opened, high-pressure fluid rushes in from upstream, but at this time the rear gate valve 6 is already closed, and the fluid can only flow to the outlet channel 9 through pipe 4 via the orifice plate 71. The throttling effect of the orifice plate 71 buffers the pressure impacting the sealing surface of the rear gate valve 6, preventing the sealing surface from directly bearing the impact under high pressure differential.

[0048] It should be noted that the pressure protection mechanism for the rear gate valve 6 during mode switching is as follows: When switching from low-flow mode to fully open mode, the rear gate valve 6 is in the closed state. The pressure before the valve (on the inlet side of pipe 3) is approximately equal to the pressure on the inlet side of pipe 4, while the pressure after the valve (on the outlet channel 9) is close to zero. To open the rear gate valve 6 at this time, the valve core must overcome this pressure difference. However, in this design, since pipe 4 and the channel containing the rear gate valve 6 (pipe 3) are connected in parallel at the outlet channel 9, and pipe 4 has a throttling orifice plate 71, the pressure before the rear gate valve 6 is actually the pressure after the throttling orifice plate 71, which is much smaller than the main pressure after the front gate valve 5. Simultaneously, during the opening process of the rear gate valve 6, its sealing surface only needs to overcome frictional resistance under a small pressure difference, avoiding the severe wear of the sealing surface caused by high-speed fluid scouring when opening a traditional gate valve under a high pressure difference.

[0049] Through the above improvements, this embodiment achieves the switching between high-flow and low-flow operating modes using a gate valve that is only used as a shut-off valve within the same fluid channel by combining the operation of a front gate valve 5 and a rear gate valve 6 with a parallel throttling pipeline. This expands the application range of the gate valve, allowing it to participate in flow distribution control while maintaining its inherent advantages of low flow resistance and high sealing performance. Furthermore, this improvement also reduces the wear and tear on the rear gate valve 6, alleviating the problem of increased maintenance costs caused by dual gate valves.

[0050] Through the above improvements, in this embodiment, in the fully closed state, the front gate valve 5 is closed and the rear gate valve 6 is open. The sealing surface of the rear gate valve 6 does not come into contact with the high-speed flowing medium, thus avoiding direct erosion by the medium. When switching from the fully closed state to the low-flow mode, the rear gate valve 6 is closed first and then the front gate valve 5 is opened, preventing the sealing surface of the rear gate valve 6 from being directly impacted and severely worn by the high-velocity medium at the moment of closure. At the same time, the throttling mechanism 7 can also prevent erosion caused by excessive pressure difference before and after the front gate valve 5 is opened. When switching from the low-flow mode to the fully open state, since the fourth pipe 4 is connected in parallel with the channel where the rear gate valve 6 is located, the pressure difference before and after the rear gate valve 6 is reduced, thereby reducing the wear of the rear gate valve 6 in all aspects. When switching from the fully open state to the fully closed state or vice versa, the transition can be made through the intermediate low-flow mode, avoiding wear on the gate valve and reducing the maintenance cost of the double gate valve.

[0051] With the above improvements, the throttling mechanism 7 in this embodiment is installed on an independent No. 4 pipe 4, becoming a module that can be disassembled and replaced separately. If it is necessary to adjust the flow rate, it is only necessary to replace a throttling mechanism 7 with a different orifice size, without modifying any main pipe or main valve.

[0052] This embodiment also provides a control method for a wear-resistant double-gate multi-channel fluid distribution gate valve, which is applied to the following control logic: When the system is in a fully closed state, the front gate valve 5 is closed and the rear gate valve 6 is open; When switching from the fully closed state to the low flow mode, the first operation sequence is executed: first close the rear gate valve 6, then open the front gate valve 5; When switching from low flow mode to high flow mode, the second operation sequence is executed: with the front gate valve 5 kept open, the rear gate valve 6 is opened; When switching from the fully closed state to the high flow mode, the third operation sequence is executed: while the rear gate valve 6 remains open, the front gate valve 5 is opened.

[0053] Example 2: According to the above embodiment 1, when the throttling mechanism 7 uses the orifice plate 71 for throttling, it is generally installed at the pipe flange connection or a reserved groove is set in the pipe in advance for installation. The former is prone to leakage during installation, while the latter has high installation cost and high precision requirements. At the same time, the excessive pressure difference between the front and rear sides when the rear gate valve 6 is opened will lead to strong erosion. Finally, after opening, there will be a problem of excessive water flow impact at the confluence of pipe 4 and pipe 3 in the outlet pipe 9.

[0054] To address the aforementioned issues, this embodiment provides a wear-resistant double-gate multi-channel fluid distribution gate valve. The difference between this embodiment and Embodiment 1 lies in the arrangement of pipe 4 and the throttling mechanism 7 within pipe 4.

[0055] Please see Figures 5-9 The fourth pipe 4 includes: Throttling mechanism 7, the throttling mechanism 7 includes a ring seat 72 and a throttling orifice plate 71 fixed on the ring seat 72, the ring seat 72 is slidably disposed in the fourth pipe 4; Drive mechanism 8 is used to drive throttling mechanism 7 to slide within pipe 4; Specifically, before the rear gate valve 6 is opened, the throttling mechanism 7 is moved backward by the drive mechanism 8, so that the high-pressure zone generated on the front side of the throttling orifice plate 71 is away from the inlet of the No. 3 pipe 3; after the rear gate valve 6 is opened, the throttling mechanism 7 is moved forward by the drive mechanism 8, so that the high-speed water flow zone generated on the rear side of the throttling orifice plate 71 is away from the outlet of the No. 3 pipe 3.

[0056] It should be noted that moving in the same direction as the fluid flow is called moving backward, and moving in the opposite direction of the fluid flow is called moving forward.

[0057] In this embodiment, as Figure 7 and Figure 8 As shown, the fourth pipe 4 includes a central pipe 41 located in the middle and side pipes 42 at both ends of the central pipe 41. The inner diameter of the central pipe 41 is larger than the inner diameter of the side pipes 42. The driving mechanism 8 includes: End cap 84, located on the outside of one side of the side tube 42, is used to drive the lead screw 81 to rotate; The lead screw 81 is installed inside the middle tube 41. Both ends of the lead screw 81 pass through the end caps at both ends of the middle tube 41, and the middle position of the lead screw 81 passes through the threaded hole of the ring seat 72 and is threadedly engaged. The guide rod 82 is installed inside the middle tube 41. Both ends of the guide rod 82 pass through the end caps at both ends of the middle tube 41, and the middle position of the lead screw 81 passes through the through hole of the ring seat 72. The lead screw 81 is connected to the end of the end cover 84 at one end, and the end cover 84 drives the lead screw 81 to rotate. The other end of the lead screw 81 is provided with an external driver 83 outside the middle tube 41 for rotating and supporting the lead screw 81. The guide rod 82 is also provided with external drivers 83 at both ends outside the middle tube 41 for rotating and supporting the guide rod 82.

[0058] In this embodiment, a motor and a transmission gear are installed inside the lead screw 81. The motor is fixed on the housing of the lead screw 81, and the transmission gear is a helical gear. Helical gears are fixed on the output shaft of the motor and the end of the lead screw 81 respectively and mesh with each other. The motor drives the lead screw 81 to rotate.

[0059] In this embodiment, as Figure 9 As shown, a groove is provided on the outer side of the ring seat 72, and a sealing ring 73 is provided in the groove, thereby achieving sealing during the sliding process of the ring seat 72.

[0060] In this embodiment, when a motor is used as the drive source, the rotational motion of the motor is transmitted to the lead screw 81 through a transmission gear. The transmission gear uses a helical gear engagement, which has a higher meshing overlap than a spur gear, enabling smoother torque transmission and reducing transmission noise. The small helical gear on the motor output shaft drives the large helical gear fixed at the end of the lead screw 81 to rotate, achieving speed reduction and torque increase. When the lead screw 81 rotates, its external thread engages with the internal threaded hole of the ring seat 72, converting the rotational motion into the linear motion of the ring seat 72. Since the ring seat 72 is also passed through by the guide rod 82, the guide rod 82 restricts the rotational freedom of the ring seat 72, ensuring that the ring seat 72 can only slide smoothly along the axial direction of pipe 4 and will not rotate circumferentially.

[0061] It should be noted that the mechanism by which the sliding of the throttling mechanism 7 affects the distribution of the high-pressure zone and the high-speed flow zone is as follows: Before the rear gate valve 6 opens, the throttling mechanism 7 is moved backward (i.e., towards the outlet channel 9) by the drive mechanism 8. At this time, the high-pressure zone on the front side of the orifice plate 71 (near the side of pipe 2) moves backward accordingly. Since the inlet of pipe 3 is located to the side of pipe 4, the backward movement of the orifice plate 71 moves the high-pressure zone away from the inlet of pipe 3, thereby reducing the pressure in front of the rear gate valve 6 (inside pipe 3) and reducing the pressure difference that needs to be overcome when the rear gate valve 6 opens. After the rear gate valve 6 opens, the throttling mechanism 7 is moved forward (i.e., towards pipe 2) by the drive mechanism 8. At this time, the high-speed flow zone formed on the rear side of the orifice plate after the fluid passes through the orifice plate 71 moves forward accordingly. After the high-speed water flow zone moves away from the outlet of pipe 3, in the water outlet channel 9, when the large-flow, low-speed water flow from pipe 3 meets the small-flow, high-speed water flow from pipe 4, the momentum difference between the two water flows decreases, and the turbulence intensity and impact force at the confluence point are significantly reduced.

[0062] It should be noted that the dynamic sealing principle of the sealing ring 73 is as follows: The sealing ring 73 is installed in the groove on the outer side of the ring seat 72. The sealing ring 73 is an O-ring rubber sealing ring with a circular cross-section. When the ring seat 72 slides inside pipe 4, the sealing ring 73 is compressed between the outer wall of the ring seat 72 and the inner wall of pipe 4, utilizing the elastic deformation of the rubber material to form a radial sealing force. In the static state, the sealing ring 73 provides a static sealing effect, preventing high-pressure fluid from leaking from the gap between the ring seat 72 and the inner wall of the pipe. In the sliding state, the sealing ring 73 relies on its elasticity to maintain contact with the inner wall of the pipe, while allowing the ring seat 72 to slide with relatively small frictional resistance. The sealing ring 73 is made of oil-resistant and wear-resistant nitrile rubber or fluororubber to adapt to long-term sliding conditions.

[0063] It should be noted that the sealing structure at the end caps of the lead screw 81, guide rod 82, and pipe section 41 includes a combined sealing structure at the point where the lead screw 81 and guide rod 82 pass through. This sealing structure comprises a skeleton oil seal and an O-ring. The skeleton oil seal prevents fluid leakage from the pipeline along the axial direction of the lead screw 81 and guide rod 82, while the O-ring seal seals the static sealing surface between the end cap and pipe section 41. The skeleton oil seal employs a double-lip structure, with the main lip facing the inside of the pipeline to prevent fluid leakage and the secondary lip facing the atmosphere to prevent external impurities from entering. The surfaces of the lead screw 81 and guide rod 82 at the point where they pass through the end caps are chrome-plated and polished, with a surface roughness Ra≤0.4μm, to reduce friction with the oil seal and extend its lifespan.

[0064] Through the above improvements, this embodiment sets the throttling mechanism 7 to slide freely within pipe 4. On the one hand, this facilitates the installation of the orifice plate 71 in the middle of the pipe. When a small flow rate continuously passes through the orifice plate, it can prevent excessive pressure on both sides of the orifice plate 71 from causing leakage at the pipe connection. On the other hand, when switching between the small flow rate and fully open modes before and after the gate valve 6 is opened, by controlling the position of the orifice plate 71, the pressure difference between the front and back sides of the gate valve 6 can be reduced when it is opened, and the impact force of the water flow at the confluence of pipe 4 and pipe 3 can be prevented from being too large after opening.

[0065] Example 3: Unlike Embodiment 2, in order to reduce the cost increase and component complexity caused by adding the drive mechanism 8, this embodiment achieves another technical effect by removing the drive mechanism 8.

[0066] This embodiment provides a wear-resistant double-gate multi-channel fluid distribution gate valve, which differs from Embodiment 2 in the setting of pipe 4 and the setting of throttling mechanism 7 inside pipe 4.

[0067] Please see Figure 1 , Figure 10 and Figure 11A throttling mechanism 7 is installed inside the fourth pipe 4, and the throttling mechanism 7 includes: The orifice plate assembly 701 is fixed at the end of pipe 4. A sliding perforated plate assembly 702 is movably connected to the front side of a fixed perforated plate assembly 701, and the sliding perforated plate assembly 702 and the fixed perforated plate assembly 701 are connected by an elastic component 703. The orifice diameter of the throttling orifice plate on the sliding orifice plate assembly 702 is larger than that of the throttling orifice plate on the fixed orifice plate assembly 701. The pressure difference inside the pipe acts on the sliding orifice plate assembly 702, enabling the sliding orifice plate assembly 702 to slide adaptively within the fourth pipe 4.

[0068] Working Principle: In low-flow mode, fluid flows in pipe 4, creating a pressure difference across the sliding orifice plate assembly 702. This pressure difference acts on the sliding orifice plate assembly 702, overcoming the spring force and causing it to move backward. Due to the movement of the sliding orifice plate assembly 702, the relative position between its central throttling orifice and the throttling orifice of the fixed orifice plate assembly 701 changes, automatically adjusting the total throttling area. The smaller the distance between the fixed orifice plate assembly 701 and the sliding orifice plate assembly 702, the stronger the throttling effect. At the instant the gate valve 6 opens, the pressure difference across pipe 4 drops sharply. The pressure difference across the sliding orifice plate assembly 702 decreases, and the sliding orifice plate assembly 702 resets forward under the spring force. During the reset process, the displacement of the sliding orifice plate assembly 702 changes the effective throttling area, gradually expanding the flow channel and smoothly transitioning to a high-flow state, avoiding water hammer impact during sudden opening.

[0069] In this embodiment, as Figure 11 As shown, the fixed orifice plate assembly 701 includes an annular seat 72a and a throttling orifice plate 71a fixed on the annular seat 72a. The annular seat 72a is fixed on the fourth pipe 4. The sliding orifice plate assembly 702 includes an annular seat 72b and a throttling orifice plate 71b fixed on the annular seat 72b. The annular seat 72b is slidably disposed in the fourth pipe 4.

[0070] It should be noted that the elastic component 703 can be either a spring or a hydraulic push rod.

[0071] It should be noted that the installation and connection structure of the elastic component 703 is as follows: The elastic component 703 uses a compression spring and is installed between the fixed orifice plate assembly 701 and the sliding orifice plate assembly 702. One end of the spring abuts against the rear end face of the ring seat 72a of the fixed orifice plate assembly 701, and the other end abuts against the front end face of the ring seat 72b of the sliding orifice plate assembly 702. Annular spring seat grooves are respectively provided on the opposite end faces of the ring seats 72a and 72b, and both ends of the spring are embedded in the spring seat grooves to prevent radial displacement or dislodgement during operation. The preload of the spring is determined according to the design working conditions, and the magnitude of the preload determines the minimum pressure difference required for the sliding orifice plate assembly 702 to begin moving. The spring is made of stainless steel (such as 304 or 316L) to meet the corrosive requirements of the working medium.

[0072] It should be noted that the adaptive sliding principle of the sliding orifice plate assembly 702 follows the principle of pressure difference balance. In low-flow mode, fluid enters pipe 4 from pipe 2, first flowing through the throttling orifice plate 71b (large orifice) of the sliding orifice plate assembly 702, and then through the throttling orifice plate 71a (small orifice) of the fixed orifice plate assembly 701. Because the orifice diameter of the throttling orifice plate 71a is smaller than that of the throttling orifice plate 71b, a larger throttling pressure drop is generated at the throttling orifice plate 71a. This pressure drop acts on the chamber between the throttling orifice plates 71a and 71b, creating a pressure difference between the front and rear sides of the sliding orifice plate assembly 702. This pressure difference, multiplied by the effective area of ​​the sliding orifice plate assembly 702, forms an axial force that pushes the sliding orifice plate assembly 702 towards the fixed orifice plate assembly 701. When this axial force is greater than the preload of the spring, the sliding orifice plate assembly 702 begins to move closer to the fixed orifice plate assembly 701, and the distance between them decreases. The reduced spacing further increases the throttling intensity of the fluid, increasing the pressure difference and thus creating a positive feedback regulation process. When the compression reaction force of the spring balances the axial force generated by the pressure difference, the sliding orifice plate assembly 702 stops moving, and the system is in a stable operating state.

[0073] It should be noted that the reset process and buffering mechanism of the elastic component 703 are as follows: When the system switches from the fully open mode to the low-flow mode, the flow rate in pipe 4 suddenly decreases, and the pressure difference before and after the orifice plate 71a decreases accordingly. The axial force on the sliding orifice plate assembly 702 decreases, and the compression reaction force of the spring is greater than the axial force, pushing the sliding orifice plate assembly 702 to move away from the fixed orifice plate assembly 701. During the reset process, the spring force is gradually released, and the moving speed of the sliding orifice plate assembly 702 is damped by the fluid, avoiding the impact caused by rapid reset. At the same time, the distance between the sliding orifice plate assembly 702 and the fixed orifice plate assembly 701 increases during the reset process, and the flow area increases, ensuring that the throttling intensity will not be too large due to the small distance in the low-flow mode. The damping effect of the spring plays a buffering role, effectively suppressing the pressure fluctuation at the moment of system switching.

[0074] It should be noted that the mechanism by which gradient throttling improves system reliability is as follows: In this embodiment, two throttling orifice plates, one large and one small, are connected in series to create a gradient throttling effect. The throttling orifice plate 71a of the fixed orifice plate assembly 701 has a small orifice diameter (e.g., d1=8mm) and undertakes the main throttling and pressure reduction function; the throttling orifice plate 71b of the sliding orifice plate assembly 702 has a large orifice diameter (e.g., d2=12mm) and plays a role in auxiliary throttling and guiding the flow pattern. When the fluid flows through the throttling orifice plate 71b, initial throttling occurs, with the flow velocity increasing and the pressure slightly decreasing; subsequently, when it flows through the throttling orifice plate 71a, the main throttling occurs, and the pressure is further reduced to the design value. This staged pressure reduction method reduces the pressure drop experienced by a single-stage orifice plate, avoiding the severe cavitation phenomenon that occurs under high pressure differential conditions. At the same time, the movement of the sliding orifice plate assembly 702 changes the effective throttling area, enabling the system to automatically adjust the throttling ratio under different operating conditions, achieving adaptability, which is not available in a single-stage fixed orifice plate.

[0075] Through the above improvements, this embodiment, by setting a fixed orifice plate assembly 701 and a sliding orifice plate assembly 702, can conveniently install a throttling orifice plate in the middle of the pipeline without using the drive mechanism 8. On the other hand, the two throttling orifice plates, one large and one small, can form a gradient throttling, avoiding excessive throttling intensity at one time, which would cause the throttling orifice plate to wear out quickly. Finally, the elastic connection between the sliding orifice plate assembly 702 and the fixed orifice plate assembly 701 can not only facilitate installation but also achieve the effect of adaptively adjusting the throttling intensity.

[0076] Although this embodiment cannot directly reduce the pressure difference between the front and rear sides of the gate valve 6 when it is opened by moving the throttling orifice plate as in Embodiment 2, its gradient throttling can effectively reduce the water pressure in the high-pressure zone generated on the front side, thereby indirectly reducing the pressure difference between the front and rear sides of the gate valve 6 when it is opened.

[0077] It should be noted that, in this document, relational terms such as "first" and "second" are used merely to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

[0078] Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A wear-resistant double-gate multi-channel fluid distribution gate valve, characterized in that, It includes a fluid distribution structure, which includes fluid pipes, and the fluid pipes include a first pipe (1), a second pipe (2), a third pipe (3), and a water outlet channel (9) connected in sequence along the fluid direction. Pipeline 1 (1) and Pipeline 3 (3) are two-way pipes and are respectively equipped with a front gate valve (5) and a rear gate valve (6). Pipeline 2 (2) and water outlet channel (9) are three-way pipes. Pipeline 2 (2) is also connected to Pipeline 4 (4). The end of Pipeline 4 (4) is connected to the water outlet channel (9). Pipeline 4 (4) is equipped with a throttling mechanism (7). When both the current gate valve (5) and the rear gate valve (6) are closed, no fluid passes through the fluid distribution structure. When the current gate valve (5) is open and the rear gate valve (6) is closed, the fluid passes through the fourth pipe (4) equipped with a throttling mechanism (7), and the fluid distribution structure provides a continuous small flow. When both the current gate valve (5) and the rear gate valve (6) are open, the fluid passes through the third pipe (3) and the fourth pipe (4) and flows into the outlet channel (9), and the fluid distribution structure provides a continuous large flow.

2. The wear-resistant double-gate multi-channel fluid distribution gate valve according to claim 1, characterized in that, The throttling mechanism (7) includes a ring seat (72) and a throttling orifice plate (71) fixed on the ring seat (72). A through hole is provided at the center of the throttling orifice plate (71), and the ring seat (72) is fixed on the flange at the end of the fourth pipe (4).

3. The wear-resistant double-gate multi-channel fluid distribution gate valve according to claim 1, characterized in that, The throttling mechanism (7) includes a throttling orifice plate that can move axially within the fourth pipe (4) for adjusting the fluid state during mode switching.

4. The wear-resistant double-gate multi-channel fluid distribution gate valve according to claim 3, characterized in that, The fourth pipe (4) includes: Throttling mechanism (7), the throttling mechanism (7) includes a ring seat (72) and a throttling orifice plate (71) fixed on the ring seat (72), the ring seat (72) being slidably disposed in the fourth pipe (4); Drive mechanism (8) is used to drive throttling mechanism (7) to slide within pipe No. 4 (4); Before the rear gate valve (6) is opened, the throttling mechanism (7) is moved backward by the drive mechanism (8) so that the high pressure zone generated in front of the throttling orifice plate (71) is far away from the inlet of the No. 3 pipeline (3); after the rear gate valve (6) is opened, the throttling mechanism (7) is moved forward by the drive mechanism (8) so that the high-speed water flow zone generated behind the throttling orifice plate (71) is far away from the outlet of the No. 3 pipeline (3).

5. The wear-resistant double-gate multi-channel fluid distribution gate valve according to claim 3, characterized in that, A throttling mechanism (7) is installed inside the fourth pipe (4), the throttling mechanism (7) comprising: The orifice plate assembly (701) is fixed at the end of pipe (4); A sliding perforated plate assembly (702) is movably connected to the front side of a fixed perforated plate assembly (701), and the sliding perforated plate assembly (702) and the fixed perforated plate assembly (701) are connected by an elastic component (703); Among them, the orifice diameter of the throttling orifice plate on the sliding orifice plate assembly (702) is larger than that of the throttling orifice plate on the fixed orifice plate assembly (701). The pressure difference inside the pipe acts on the sliding orifice plate assembly (702), enabling the sliding orifice plate assembly (702) to slide adaptively within the fourth pipe (4).

6. The wear-resistant double-gate multi-channel fluid distribution gate valve according to claim 4, characterized in that, The fourth pipe (4) includes a central pipe (41) located in the middle and side pipes (42) at both ends of the central pipe (41). The inner diameter of the central pipe (41) is larger than the inner diameter of the side pipes (42). The driving mechanism (8) includes: An external driver (83) is located on the outside of one of the side tubes (42) and is used to drive the lead screw (81) to rotate. The lead screw (81) is installed inside the middle tube (41). The two ends of the lead screw (81) pass through the end caps at both ends of the middle tube (41), and the middle position of the lead screw (81) passes through the threaded hole of the ring seat (72) and is threadedly engaged. The guide rod (82) is set inside the middle tube (41). The two ends of the guide rod (82) pass through the end caps at both ends of the middle tube (41), and the middle position of the lead screw (81) passes through the through hole of the ring seat (72). The lead screw (81) is connected to the external driver (83) at one end, which is close to the external driver (83). The external driver (83) drives the lead screw (81) to rotate. The other end of the lead screw (81) is provided with an end cap (84) outside the middle tube (41) for rotating and supporting the lead screw (81). The guide rod (82) is also provided with end caps (84) at both ends outside the middle tube (41) for rotating and supporting the guide rod (82).

7. A wear-resistant double-gate multi-channel fluid distribution gate valve according to claim 6, characterized in that, The outer side of the ring seat (72) is provided with a groove, and a sealing ring (73) is provided in the groove.

8. A wear-resistant double-gate multi-channel fluid distribution gate valve according to claim 5, characterized in that, The elastic component (703) is a compression spring and is installed between the fixed orifice plate assembly (701) and the sliding orifice plate assembly (702).

9. A wear-resistant double-gate multi-channel fluid distribution gate valve according to claim 8, characterized in that, The fixed perforated plate assembly (701) and the sliding perforated plate assembly (702) are respectively provided with annular spring seat grooves on their opposite end faces, and the two ends of the spring are respectively embedded in the spring seat grooves.

10. A control method for a wear-resistant double-gate multi-channel fluid distribution gate valve, applied to the wear-resistant double-gate multi-channel fluid distribution gate valve as described in any one of claims 1-9, characterized in that, Includes the following control logic: When the system is in a fully closed state, the front gate valve (5) is closed and the rear gate valve (6) is open; When switching from the fully closed state to the low flow mode, the first operation sequence is executed: first close the rear gate valve (6), then open the front gate valve (5). When switching from low flow mode to high flow mode, the second operation sequence is executed: while the front gate valve (5) remains open, the rear gate valve (6) is opened. When switching from the fully closed state to the high flow mode, the third operation sequence is executed: while the rear gate valve (6) remains open, the front gate valve (5) is opened.

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