Check valve and pipe water delivery system

Abstract

The application relates to the technical field of fluid delivery, in particular to a check valve and a pipeline water delivery system. The check valve is arranged in a pipeline, and the check valve comprises a valve body and a gate. Along the axial direction of the valve body, the valve body is provided with a fluid passage; a flowmeter is arranged in the pipeline to detect the fluid flow in the pipeline; a driving mechanism is arranged in the valve body and selectively electrically connected with the flowmeter; the gate is connected with the driving end of the driving mechanism, and the gate is moved relative to the valve body along a first direction and has a first position and a second position. The driving mechanism drives the gate to move between the first position and the second position. When the gate is in the first position, the gate is located outside the fluid passage. When the gate is in the second position, the gate is inserted into the fluid passage and blocks the fluid passage. The first direction is perpendicular to the axial direction of the valve body. The check valve can easily cut off the water flow, and can reduce the phenomenon of water hammer caused by pressure reduction.

Description

Technical Field

[0001] This application relates to the field of fluid transport technology, and in particular to a check valve and a pipeline water transport system. Background Technology

[0002] In pumped water supply systems, check valves are installed at the pump outlet to prevent backflow of water after pump shutdown. Many types of check valves are available, such as swing check valves, silent check valves, quiet check valves, axial flow check valves, counterweight slow-closing check valves, hydraulically controlled slow-closing butterfly valves, hydraulically controlled slow-closing eccentric ball valves, and multi-functional pump control valves. All these check valves have a valve disc that moves in the direction of water flow. When the pump stops due to power failure, it generates the first pressure drop water hammer. Simultaneously, the valve disc begins to close. The rotation of the valve disc during closure disturbs the water flow. This disturbance not only changes the direction of water flow after pump shutdown but also alters the flow velocity. These two changes result in a significant change in flow velocity. Therefore, after the pump stops, the system experiences a second water hammer. The first and second water hammers overlap and are transmitted towards the end in the form of a pressure-reducing wave, causing negative pressure along the pipeline. Negative pressure not only damages the pipeline lining, but severe negative pressure can also cause the pipeline to collapse. At the same time, water vaporization and water column separation may occur, which may produce severe water hammer. The reflection at the end will form a pressure-boosting wave, causing a water hammer that increases pressure, and may even lead to pipeline rupture. Summary of the Invention

[0003] This application provides a check valve and a pipeline water supply system that enables the gate to more easily cut off the water flow and reduces the phenomenon of pressure drop and water hammer.

[0004] To achieve the above objectives, the main technical solutions adopted in this application include:

[0005] In a first aspect, embodiments of this application provide a check valve disposed in a pipeline. The check valve includes a valve body and a gate. Along the axial direction of the valve body, the valve body has a fluid passage. A flow meter is disposed in the pipeline to detect the fluid flow rate in the pipeline. A drive mechanism is disposed in the valve body and selectively electrically connected to the flow meter. The gate is connected to the drive end of the drive mechanism. Along a first direction, the gate moves relative to the valve body and has a first position and a second position. When the gate is in the first position, the gate is located outside the fluid passage. When the gate is in the second position, the gate is inserted into the fluid passage and blocks the fluid passage. The first direction is perpendicular to the axial direction of the valve body.

[0006] In the check valve proposed in this application embodiment, when the drive mechanism is electrically connected to the flow meter, the flow meter transmits the flow signal to the drive mechanism. The drive end of the drive mechanism drives the gate to move between a first position and a second position, thereby driving the gate to connect or block the fluid channel. When the gate is in the first position, it is located outside the fluid channel. The gate does not affect the fluid flow, and the medium in the fluid channel does not contact the gate, reducing the chance of the gate being corroded by the medium. When it is necessary to close the check valve, the drive mechanism drives the gate to move from the outside of the fluid channel to the inside of the fluid channel along a first direction, blocking the fluid flow. During the movement of the gate along the first direction, when it is inside the fluid channel, the movement direction of the gate is perpendicular to the fluid flow direction, resulting in less disturbance to the fluid flow and less change in fluid velocity, thus generating less pressure drop and water hammer. Furthermore, during the movement of the gate from the first position to the second position, since the movement direction of the gate is perpendicular to the fluid flow direction, the resistance generated by the fluid flow on the movement of the gate is small, making it easier for the gate to close and block the fluid flow.

[0007] Optionally, the valve body includes a first valve body and a second valve body, and the fluid passage includes a first fluid passage and a second fluid passage. The first valve body further includes a first body portion and a first valve seat, the first valve seat surrounding the first fluid passage, and the first body portion sleeved on the outside of the first valve seat. The second valve body further includes a second body portion and a second valve seat, the second valve seat surrounding the second fluid passage, and the second body portion sleeved on the outside of the second valve seat. When the gate is in the first position, the first valve seat and the second valve seat abut against each other along the axial direction of the valve body. When the gate is in the second position, the gate squeezes the first valve seat and the second valve seat along the axial direction of the valve body to extend between the first fluid passage and the second fluid passage.

[0008] In the above embodiments, when the gate is in the first position, the first fluid channel and the second fluid channel are connected, and the first valve seat and the second valve seat abut against each other along the axial direction of the valve body, which can seal the fluid channel and reduce fluid leakage; when the gate is in the second position, the first valve seat and the second valve seat press against the gate to form a seal.

[0009] Optionally, both the first valve seat and the second valve seat are constructed as elastic elements.

[0010] In the above embodiments, the first valve seat and the second valve seat can be elastically deformed when squeezed and form a seal, ensuring that the fluid channel has good sealing performance in both the flow and blockage states.

[0011] Optionally, the first valve seat and the second valve seat each have a first end and a second end facing each other. When the gate is in the first position, the outer periphery of the first end and the outer periphery of the second end form a first guide groove, and the cross-sectional area of ​​the first guide groove gradually increases along the radial direction of the valve body. When the gate is in the first position, the inner periphery of the first end and the inner periphery of the second end form a second guide groove, and the cross-sectional area of ​​the second guide groove gradually decreases along the radial direction of the valve body.

[0012] In the above embodiment, the cross-sectional area of ​​the first guide groove gradually decreases from the outside to the inside of the valve body, and the cross-sectional area of ​​the second guide groove gradually decreases from the inside to the outside of the valve body. This provides guidance for the movement of the gate in the first direction, enabling the gate to cut off the fluid in a direction perpendicular to the fluid flow, and ensuring that the gate does not deviate when moving. This reduces the impact of the gate on the first and second valve seats, thereby improving the sealing performance of the check valve.

[0013] Optionally, the first valve seat includes a first segment and a second segment, and the second valve seat includes a third segment and a fourth segment connected together. Along the axial direction of the valve body, the first segment is connected to the second segment, and the third segment is connected to the fourth segment. When the gate is in the first position, the second segment abuts against the third segment. Along the radial direction of the valve body, the thickness of the first segment is less than the thickness of the second segment, and the thickness of the fourth segment is less than the thickness of the third segment.

[0014] In the above embodiment, the strength of the first segment is less than that of the second segment, and the strength of the fourth segment is less than that of the third segment. The strength of the second and third segments is stronger, which can ensure the sealing effect. The strength of the first and fourth segments is smaller, making them easier to shrink. When the gate squeezes the first valve seat and the second valve seat to move in the first direction, the friction force on the gate can be reduced.

[0015] Optionally, from the first segment to the second segment, the thickness of the first segment gradually increases along the radial direction of the valve body; from the fourth segment to the third segment, the thickness of the fourth segment gradually increases along the radial direction of the valve body.

[0016] In the above embodiments, the first segment can have both deformation capability and sufficient strength, and the fourth segment can have both deformation capability and sufficient strength.

[0017] Optionally, along the first direction, the gate includes a connected main body and a first guide portion, and the cross-sectional area of ​​the first guide portion gradually decreases along the first direction from the main body to the first guide portion.

[0018] In the above embodiments, the first guide portion cooperates with the first guide groove and the second guide groove to provide guidance for the movement of the gate along the first direction.

[0019] Optionally, the flow meter has a detection section located inside the pipe for detecting the fluid flow rate inside the pipe.

[0020] Optionally, the drive mechanism includes a power component and an actuator, the power component being electrically connected to the flow meter; the actuator being connected to the power component and the gate, to drive the gate to move between the first position and the second position.

[0021] Optionally, the power assembly includes a pressure source containing a medium; the drive mechanism further includes a solenoid valve selectively electrically connected to the flow meter, the solenoid valve having an air inlet, a first air inlet, and a second air inlet, the air inlet communicating with the pressure source; the actuator includes a housing and a piston, the housing being connected to the valve body, the piston being disposed within the housing and dividing the housing into a first cavity and a second cavity, the first air inlet communicating with the first cavity, the second air inlet communicating with the second cavity, and the piston being connected to the gate to drive the gate to move between the first position and the second position.

[0022] Secondly, embodiments of this application provide a pipeline water supply system, including the check valve described in any of the above embodiments.

[0023] The pipeline water supply system in the above embodiments includes the check valve described in any of the above embodiments and has the beneficial effects of the check valve described in any of the above embodiments. Attached Figure Description

[0024] To more clearly illustrate the technical solutions in the specific embodiments of this application or the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this application. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0025] Figure 1 This is a schematic diagram of the check valve in one embodiment of this application, wherein the gate is in the first position;

[0026] Figure 2 This is a schematic diagram of the check valve in one embodiment of this application, wherein the gate is in the second position;

[0027] Figure 3 This is a schematic diagram of the structure of the first valve seat and the second valve seat in one embodiment of this application;

[0028] Figure 4 for Figure 3 Enlarged view of region E in the middle;

[0029] Figure 5 for Figure 1 Enlarged view of region D in the middle;

[0030] Figure 6 This is a hydraulic model diagram of a pipeline water conveyance system in one embodiment of this application;

[0031] Figure 7 This is a steady-state hydraulic gradient diagram of a pipeline water conveyance system in one embodiment of this application;

[0032] Figure 8 The water hammer pressure envelope diagram for a pipeline water supply system using a slow-closing hydraulic butterfly valve with a traditional check valve when the pump stops due to a malfunction.

[0033] Figure 9 A diagram showing the water hammer pressure envelope when a pump stops due to a malfunction in a pipeline water supply system using a silent check valve (a traditional check valve).

[0034] Figure 10 The water hammer pressure envelope diagram of a pipeline water supply system using a check valve in one embodiment of this application when the pump stops due to a fault;

[0035] Figure 11 This is a graph showing the change in pump speed when the pump stops due to a fault in a pipeline water supply system using a check valve in one embodiment of this application.

[0036] [Explanation of Labels in the Attached Image]

[0037] 1. Valve body; 10. Fluid passage; 11. First body section; 111. First flange; 112. Second flange; 12. First valve seat; 121. First end; 122. First section; 123. Second section; 13. Second body section; 131. Third flange; 132. Fourth flange; 14. Second valve seat; 141. Second end; 142. Third section; 143. Fourth section; 15. First guide groove; 16. Second guide groove;

[0038] 2. Gate; 21. Main body; 22. First guide section;

[0039] 31. Sealing element; 32. Cover plate; 33. O-ring seal;

[0040] 4. Solenoid valve; P. Air inlet; A. First air outlet; B. Second air outlet; 41. Air inlet pipe; 42. First exhaust pipe; 43. Second exhaust pipe; 44. First solenoid coil; 45. Second solenoid coil;

[0041] 5. Pressure source;

[0042] 6. Flow meter; 61. Testing department;

[0043] 7. Actuator; 71. Housing; 72. Piston; 73. First cavity; 74. Second cavity;

[0044] 8. Current switch;

[0045] 100. Pipeline;

[0046] X, the axial direction of the valve body; Y, the first direction. Detailed Implementation

[0047] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0048] Unless otherwise defined, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains; the terminology used in the description of this application is for the purpose of describing particular embodiments only and is not intended to limit the application; the terms "comprising" and "having," and any variations thereof, in the description, claims, and accompanying drawings of this application are intended to cover non-exclusive inclusion. The terms "first," "second," etc., in the description, claims, or accompanying drawings of this application are used to distinguish different objects, not to describe a specific order or hierarchy.

[0049] In this application, the reference to "embodiment" means that a specific feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places throughout the specification does not necessarily refer to the same embodiment, nor is it a mutually exclusive, independent, or alternative embodiment. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described in this application can be combined with other embodiments.

[0050] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "attachment" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0051] In this application, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, or B existing alone. Additionally, in this application, the character " / " generally indicates that the preceding and following related objects have an "or" relationship.

[0052] In this application, "multiple" refers to two or more (including two), similarly, "multiple sets" refers to two or more (including two sets), and "multiple pieces" refers to two or more (including two pieces).

[0053] Scientist Zhukovsky summarized a formula for calculating direct water hammer. =-a / g× Where 'a' is the propagation speed of the water hammer wave in water, and for metal pipes, for example, the average propagation speed of the water hammer wave in a steel pipe is 1000 m / s, and 'g' is the acceleration due to gravity, g = 9.81 ≈ 10 m / s². 2 ,but =-100 ,in Since this is the change in fluid velocity, we can conclude that water hammer is caused by changes in flow velocity; the greater the change in velocity, the larger the water hammer. In physics, velocity is a directional vector, and changes in both the direction and magnitude of flow velocity will cause changes in velocity value. The occurrence of this phenomenon is due to the fact that traditional check valves typically have a movable valve disc aligned with the water flow direction. When the water pump stops due to power failure, a first pressure drop and water hammer occur. Simultaneously, the movable valve disc of the check valve begins to close. During this closing process, the movable valve disc rotates, causing disturbance to the water flow. This disturbance not only alters the direction of water flow after the pump stops but also changes the flow velocity. These two changes result in a change in flow velocity. Therefore, after the pump stops, the system experiences a second water hammer. The first and second water hammers overlap and propagate towards the end in the form of a pressure-reducing wave, causing negative pressure along the pipeline. Negative pressure not only damages the pipeline lining, but severe negative pressure can also cause the pipeline to collapse. At the same time, water vaporization and water column separation may occur, which may produce severe water hammer. Furthermore, the reflection at the end will form a pressure-boosting wave, causing a pressure-boosting water hammer, and may even lead to pipeline rupture.

[0054] Therefore, in current pipeline water supply systems, using traditional check valves as devices to prevent backflow of water after pump shutdown may exacerbate water hammer during pump stoppage, posing a serious safety hazard. To reduce this serious safety hazard, more diversified and complex water hammer protection measures must be adopted, but this will also significantly increase costs.

[0055] In view of this, this application provides a check valve in which the movement direction of the movable gate is perpendicular to the fluid flow direction, which reduces the resistance encountered during the valve closing process, makes it easier to close the valve, and can reduce the disturbance to the water flow, thereby reducing pressure drop and water hammer.

[0056] Firstly, reference Figure 1 and Figure 2 This application provides a check valve disposed in a pipeline 100. The check valve includes a valve body 1 and a gate 2. Along the axial direction X of the valve body 1, the valve body 1 has a fluid passage 10. A flow meter 6 is disposed in the pipeline 100 to detect the fluid flow rate in the pipeline 100. A drive mechanism is disposed in the valve body 1 and selectively electrically connected to the flow meter 6. The gate 2 is connected to the drive end of the drive mechanism. Along the first direction Y, the gate 2 moves relative to the valve body 1 and has a first position and a second position. The drive mechanism drives the gate 2 to move between the first position and the second position. When the gate 2 is in the first position, the gate 2 is located outside the fluid passage 10. When the gate 2 is in the second position, the gate 2 is inserted into the fluid passage 10 and blocks the fluid passage 10. The first direction Y is perpendicular to the axial direction X of the valve body 1.

[0057] The flow meter 6 is installed in the pipe 100 to detect the fluid flow rate in the pipe 100. When the fluid flow rate in the pipe 100 reaches the set value, the drive mechanism is electrically connected to the flow meter. The flow meter 6 transmits the flow signal to the drive mechanism. The drive end of the drive mechanism drives the gate 2 to move between the first position and the second position, so as to drive the gate 2 to connect or block the fluid channel 10.

[0058] The check valve proposed in this embodiment has a valve body 1 with a fluid passage 10 for fluid flow. When the gate 2 is in the first position, the gate 2 is completely outside the fluid passage 10, the fluid passage 10 is in a connected state, the gate 2 does not affect the fluid flow, and the medium in the fluid passage 10 does not contact the gate 2, which can reduce the probability of the gate 2 being corroded by the medium. When the gate 2 is in the second position, the fluid passage 10 is blocked by the gate 2, the fluid passage 10 is closed, thereby blocking the fluid. When it is necessary to close the check valve, it is only necessary to move the gate 2 from the outside of the fluid passage 10 to the inside of the fluid passage 10 along the first direction Y to block the fluid flow. During the movement of the gate 2 along the first direction Y, when it is inside the fluid passage 10, the movement direction of the gate 2 is perpendicular to the fluid flow direction, the disturbance to the fluid flow is small, the change in fluid velocity is also small, and therefore the pressure drop water hammer is small. Furthermore, as the gate 2 moves from the first position to the second position, since the direction of movement of the gate 2 is perpendicular to the direction of fluid flow, the resistance generated by the fluid flow on the movement of the gate 2 is small, making it easier for the gate 2 to close and block the fluid flow.

[0059] It should be noted that the first direction Y is perpendicular to the axial direction X of the valve body 1. The first direction Y can be any radial direction of the valve body 1, as long as the first direction Y is perpendicular to the fluid flow direction in the fluid channel 10.

[0060] The flow meter 6 can be any type of flow detection device, as long as it can detect the flow in the pipe 100 and transmit the flow signal to the drive mechanism, and then control the gate 2 to move between the first position and the second position through the drive mechanism.

[0061] For example, when the flow meter 6 detects that the flow rate in the pipe 100 is zero or close to zero, and the flow velocity in the pipe is also zero or close to zero, the flow meter 6 is electrically connected to the drive mechanism. The drive mechanism controls the gate 2 to move from the first position to the second position to block the fluid channel and cut off the water flow. Since the direction of movement of the gate 2 along the first direction Y is perpendicular to the fluid flow direction, and the fluid channel 10 is blocked instantaneously when the flow rate or flow velocity is close to zero, there is no disturbance to the fluid during the instantaneous valve closing process, or the disturbance to the fluid is negligible. That is, the valve closing process does not change the fluid flow direction or the fluid flow rate, so there is no change in flow velocity. Therefore, after the pump stops, the pipeline water supply system does not generate a second pressure-reducing water hammer. The system only has one pressure-reducing water hammer generated by the pump itself stopping. Therefore, the pressure-reducing water hammer generated by the check valve in this application after the pump stops is much smaller than that generated by the traditional check valve. The pipeline water supply system is also correspondingly safer and more reliable. The water hammer protection measures in this application are simple and reduce costs.

[0062] Optionally, refer to Figure 1 and Figure 2 The valve body 1 includes a first valve body and a second valve body. The fluid channel 10 includes a first fluid channel and a second fluid channel. The first fluid channel is located in the first valve body, and the second fluid channel is located in the second valve body. When the gate 2 is inserted into the fluid channel 10, the gate 2 is located between the first valve body and the second valve body to block the first fluid channel and the second fluid channel.

[0063] The first valve body and the second valve body are connected, and a channel for the gate 2 to move is formed between the first valve body and the second valve body. When the gate 2 is in the first position, the first fluid channel and the second fluid channel are connected. When the gate 2 is in the second position, the gate 2 is located between the first valve body and the second valve body, and the first fluid channel and the second fluid channel are blocked.

[0064] Optionally, refer to Figure 1 and Figure 3The first valve body further includes a first body portion 11 and a first valve seat 12. The first valve seat 12 encloses a first fluid channel, and the first body portion 11 is sleeved on the outside of the first valve seat 12. The second valve body further includes a second body portion 13 and a second valve seat 14. The second valve seat 14 encloses a second fluid channel, and the second body portion 13 is sleeved on the outside of the second valve seat 14. When the gate 2 is in the first position, the first valve seat 12 and the second valve seat 14 abut against each other along the axial direction X of the valve body 1. When the gate 2 is in the second position, the gate 2 squeezes the first valve seat 12 and the second valve seat 14 along the axial direction X of the valve body 1 to extend between the first fluid channel and the second fluid channel.

[0065] When the gate 2 is in the first position, the first fluid channel and the second fluid channel are connected, and the first valve seat 12 and the second valve seat 14 abut against each other along the axial direction X of the valve body 1, which can seal the fluid channel 10 and reduce fluid leakage. When the check valve needs to be closed, the gate 2 moves from the outside of the fluid channel 10 towards the inside of the fluid channel 10 along the first direction Y. When the gate 2 contacts the first valve seat 12 and the second valve seat 14, the gate 2 is squeezed into the space between the first valve seat 12 and the second valve seat 14, and squeezes the first valve seat 12 and the second valve seat 14 along the axial direction X of the valve body 1, so that the first valve seat 12 and the second valve seat 14 form a pressure seal with the gate 2. That is, when the gate 2 is in the second position, the gate 2 is pressed against the space between the first valve seat 12 and the second valve seat 14.

[0066] Optionally, both the first valve seat 12 and the second valve seat 14 are constructed as elastic elements. The first valve seat 12 and the second valve seat 14 can undergo elastic deformation when compressed, forming a seal to ensure good sealing performance of the fluid passage 10 in both flowing and blocked states. Exemplarily, the first valve seat 12 and the second valve seat 14 can be made of rubber material.

[0067] For example, along the axial direction X of the valve body 1, the natural length of the first valve seat 12 is L1, and the natural length of the second valve seat 14 is L2. When the first valve seat 12 and the second valve seat 14 are respectively installed on the first body portion 11 and the second body portion 13, and the first valve seat 12 and the second valve seat 14 abut against each other along the axial direction X of the valve body 1 to achieve a seal, the length of the first valve seat 12 along the axial direction X of the valve body 1 is compressed to L3, and the length of the second valve seat 14 along the axial direction X of the valve body 1 is compressed to L4, forming a strong sealing force between the first valve seat 12 and the second valve seat 14. When the gate 2 moves along the first direction Y to block the first fluid passage and the second fluid passage, the gate 2 squeezes the first valve seat 12 and the second valve seat 14, compressing the length of the first valve seat 12 along the axial direction X of the valve body 1 to L5, and the length of the second valve seat 14 along the axial direction X of the valve body 1 to L6, thereby forming a good seal between the gate 2 and the first valve seat 12 and the second valve seat 14.

[0068] Optionally, refer to Figure 3 and Figure 4 The first valve seat 12 and the second valve seat 14 have a first end 121 and a second end 141 facing each other. When the gate 2 is in the first position, the outer periphery of the first end 121 and the outer periphery of the second end 141 form a first guide groove 15. Along the radial direction of the valve body 1, the cross-sectional area of ​​the first guide groove 15 gradually increases.

[0069] When the gate 2 is in the first position, it is located outside the fluid passage 10. Along the axial direction X of the valve body 1, the first end 121 of the first valve seat 12 and the second end 141 of the second valve seat 14 abut against each other, and a first guide groove 15 is formed on the outer periphery of the first end 121 and the outer periphery of the second end 141. The cross-sectional area of ​​the first guide groove 15 gradually increases along the radial direction of the valve body 1. It should be noted that the radial direction of the valve body 1 is unidirectional, specifically from the center of the valve body 1 to the outside of the valve body 1, that is, from the outside of the valve body 1 to the inside of the valve body 1. The cross-sectional area of ​​the first guide groove 15 gradually decreases. The first guide groove 15 provides guidance for the movement of the gate 2 along the first direction Y, so that the gate 2 can cut off the fluid in a direction perpendicular to the fluid flow and prevent the gate 2 from deviating during movement, reducing the impact of the gate 2 on the first valve seat 12 and the second valve seat 14, thereby improving the sealing performance of the check valve. For example, the first guide groove 15 can be constructed as a V-shaped structure.

[0070] Optionally, refer to Figure 3 and Figure 4 When the gate 2 is in the first position, the inner circumference of the first end 121 and the inner circumference of the second end 141 form a second guide groove 16, and the cross-sectional area of ​​the second guide groove 16 gradually decreases along the radial direction of the valve body 1.

[0071] It should be noted that the radial direction of valve body 1 is unidirectional, specifically from the center of valve body 1 to the outside of valve body 1, that is, from the inside to the outside of valve body 1. The cross-sectional area of ​​the second guide groove 16 gradually decreases. The second guide groove 16 guides the movement of gate 2 along the first direction Y, enabling gate 2 to cut off the fluid in a direction perpendicular to the fluid flow, and preventing gate 2 from deviating during movement. This reduces the impact of gate 2 on the first valve seat 12 and the second valve seat 14, thereby improving the sealing performance of the check valve. For example, the second guide groove 16 can be constructed as a V-shaped structure.

[0072] It should be understood that the outer and inner circumferences of the side where the first end 121 and the second end 141 abut against each other are respectively provided with a first guide groove 15 and a second guide groove 16. When the gate 2 moves along the first direction Y, the first guide groove 15 provides guidance for the gate 2 to enter the fluid channel 10, and the second guide groove 16 provides guidance for the gate 2 to be squeezed out of the fluid channel 10.

[0073] For example, the first end 121 has a first end face, and the second end 141 has a second end face. The first end face includes a first sub-face, a second sub-face, and a third sub-face connected in sequence. The second end face includes a fourth sub-face, a fifth sub-face, and a sixth sub-face connected in sequence. When the gate 2 is in the first position, the second sub-face abuts against the fifth sub-face. The first sub-face and the fourth sub-face are angled to form a first guide groove 15, and the third sub-face and the sixth sub-face are angled to form a second guide groove 16.

[0074] Optionally, refer to Figure 3 The first valve seat 12 includes a first segment 122 and a second segment 123, and the second valve seat 14 includes a third segment 142 and a fourth segment 143 connected together. Along the axial direction X of the valve body 1, the first segment 122 is connected to the second segment 123, and the third segment 142 is connected to the fourth segment 143. When the gate 2 is in the first position, the second segment 123 abuts against the third segment 142. Along the radial direction of the valve body 1, the thickness of the first segment 122 is less than the thickness of the second segment 123, and the thickness of the fourth segment 143 is less than the thickness of the third segment 142.

[0075] Along the radial direction of the valve body 1, the thickness of the first segment 122 is less than the thickness of the second segment 123, making the strength of the first segment 122 less than the strength of the second segment 123. The thickness of the fourth segment 143 is less than the thickness of the third segment 142, making the strength of the fourth segment 143 less than the strength of the third segment 142. The strength of the second segment 123 and the third segment 142 is relatively strong, which can ensure the sealing effect. When the first valve seat 12 and the second valve seat 14 are squeezed and deformed, the first segment 122 and the fourth segment 143, which have lower strength, are easier to shrink. Furthermore, when the gate plate 2 squeezes the first valve seat 12 and the second valve seat 14 to move along the first direction Y, it can reduce the frictional force on the gate plate 2.

[0076] Optionally, refer to Figure 3 From the first segment 122 to the second segment 123, the thickness of the first segment 122 gradually increases along the radial direction of the valve body 1; from the fourth segment 143 to the third segment 142, the thickness of the fourth segment 143 gradually increases along the radial direction of the valve body 1.

[0077] From the first segment 122 to the second segment 123, the thickness of the first segment 122 gradually increases along the radial direction of the valve body 1. While ensuring that the first valve seat 12 has sufficient strength, it also makes the first valve seat 12 easy to compress, thereby reducing the frictional force of the first valve seat 12 on the gate 2. From the fourth segment 143 to the third segment 142, the thickness of the fourth segment 143 gradually increases along the radial direction of the valve body 1. While ensuring that the second valve seat 14 has sufficient strength, it also makes the second valve seat 14 easy to compress, thereby reducing the frictional force of the second valve seat 14 on the gate 2.

[0078] Optionally, refer to Figure 5Along the first direction Y, the gate 2 includes a main body 21 and a first guide 22 connected together. From the main body 21 to the first guide 22, the cross-sectional area of ​​the first guide 22 gradually decreases along the first direction Y.

[0079] The first guide portion 22 cooperates with the first guide groove 15 and the second guide groove 16 to provide guidance for the movement of the gate 2 along the first direction Y. For example, the first guide portion 22 is configured as a V-shape.

[0080] In one specific embodiment, along the axial direction X of the valve body 1, a first flange 111 is provided at the end of the first body portion 11 away from the second body portion 13, a second flange 112 is provided at the end of the first body portion 11 near the second body portion 13, a third flange 131 is provided at the end of the second body portion 13 away from the first body portion 11, and a fourth flange 132 is provided at the end of the second body portion near the first body portion 11. The first flange 111 is used to connect the first body portion 11 to the pipe 100, the third flange 131 is used to connect the second body portion to the pipe 100, the second flange 112 and the fourth flange 132 connect the first body portion 11 and the second body portion 13, and a channel for the gate plate 2 to move along the first direction Y is formed between the first body portion 11 and the second body portion 13. Along the axial direction X of the valve body 1, the size of the channel is equal to or nearly equal to the size of the gate plate 2, so as to provide guidance for the movement of the gate plate 2 along the first direction Y. A sealing element 31 is also provided between the second flange 112 and the fourth flange 132. The sealing element 31 is square in shape and has an opening in the middle for the gate 2 to pass through. The gate 2 passes through the opening of the sealing element 31 and is tightly fitted with the sealing element 31 without any gap, so that the medium in the fluid passage 10 will not leak through the gate 2.

[0081] For example, the second flange 112 has a first groove and a second groove, and the fourth flange 132 has a third groove and a fourth groove. The first groove, the second groove, the third groove, and the fourth groove together enclose a channel for the gate 2 to move along the first direction Y. The channel enclosed by the third groove and the fourth groove surrounds the fluid channel 10, and the channel enclosed by the first groove and the second groove is farther away from the fluid channel 10 than the channel enclosed by the third groove and the fourth groove. The dimension of the channel enclosed by the first groove and the second groove along the axial direction X of the valve body 1 is larger than the dimension of the channel enclosed by the third groove and the fourth groove along the axial direction X of the valve body 1, so that the seal 31 is disposed within the channel enclosed by the first groove and the second groove. The second flange 112 and the fourth flange 132 are also provided with cover plates 32 connected to the second flange 112 and the fourth flange 132. One of the cover plates 32 covers the outside of the seal 31 to limit the seal 31.

[0082] For example, refer to Figure 5If the fluid flows from the first valve body to the second valve body, i.e., the water pump is located on the side closer to the first valve body, the second valve body is provided with a circular groove, and an O-ring seal 33 is provided in the circular groove. When the check valve is in the closed state, that is, when the gate 2 is in the second position, the gate 2 has a tendency to shift towards the second valve body, so that the gate 2 and the O-ring seal 33 form a tight contact without gap, thereby improving the sealing performance of the check valve.

[0083] The first valve seat 12 and the second valve seat 14 are each provided with a first connecting part at the ends away from each other. The first connecting part is constructed as a flange structure extending radially outward along the valve body 1. The first connecting part of the first valve seat 12 is connected between the pipe 100 and the first flange 111, and the first connecting part of the second valve seat 14 is connected between the pipe 100 and the third flange 131, so as to fix the first valve seat 12 and the second valve seat 14.

[0084] Optionally, refer to Figure 1 and Figure 2 The flow meter 6 has a detection unit 61 located inside the pipe 100, which is used to detect the fluid flow rate inside the pipe 100. The detection unit 61 is located in the pipe 100 and detects changes in the fluid flow rate parameters inside the pipe 100. The flow meter 6 can be a current switch.

[0085] Optionally, the drive mechanism includes a power component and an actuator 7. The power component is electrically connected to the flow meter 6. The actuator 7 is connected to the power component and to the gate 2 to drive the gate 2 to move between a first position and a second position. The power component drives the actuator 7 to move, and the actuator 7 drives the gate 2 to move between the first and second positions to open or close the check valve. The power component can be an electric push rod; it can also be a motor. The actuator 7 is a gear and rack assembly, with the gear connected to the drive end of the motor and the rack connected to the gate 2. The motor drives the gear to rotate, which in turn drives the rack to move, causing the gate 2 to move between the first and second positions. Alternatively, the actuator 7 can be a lead screw and nut assembly, with the lead screw connected to the drive end of the motor and the nut connected to the gate 2. The motor rotation drives the lead screw to rotate, simultaneously moving the nut linearly, which in turn moves the gate 2 between the first and second positions.

[0086] Optionally, refer to Figure 1 and Figure 2The power assembly includes a pressure source 5 containing a medium. The drive mechanism also includes a solenoid valve 4, which is selectively electrically connected to a flow meter 6. The solenoid valve 4 has an inlet port P, a first outlet port A, and a second outlet port B. The inlet port P is connected to the pressure source 5. The actuator 7 includes a housing 71 and a piston 72. The housing 71 is connected to the valve body 1. The piston 72 is located inside the housing 71 and divides the housing 71 into a first cavity 73 and a second cavity 74. The first outlet port A is connected to the first cavity 73, and the second outlet port B is connected to the second cavity 74. The piston 72 is connected to a gate 2 to drive the gate 2 to move between a first position and a second position.

[0087] After the pump stops, when the flow meter 6 detects that the flow rate in the pipeline 100 has reached the preset value, the flow meter 6 transmits a signal to the solenoid valve 4. After the solenoid valve 4 is connected to the current, it generates magnetic force. The first vent A of the solenoid valve 4 opens and the second vent B closes. The medium in the pressure source 5 enters the first chamber 73. The medium pressure in the first chamber 73 is greater than the medium pressure in the second chamber 74. The medium pressure in the first chamber 73 pushes the piston 72 to compress the medium in the second chamber 74, thereby pushing the gate 2 to move from the first position to the second position.

[0088] When the pump is restarted, the first outlet A of the solenoid valve 4 gradually closes and the second outlet B gradually opens until the reading of the flow meter 6 is greater than zero. At this time, the flow meter 6 is disconnected from the solenoid valve 4, the first outlet A is completely closed, and the second outlet B is completely open. The pressure of the medium entering the second chamber 74 is greater than the pressure of the medium in the first chamber 73. The medium in the second chamber 74 pushes the piston 72 to compress the medium in the first chamber 73, causing the gate 2 to move from the first position to the second position. The fluid channel 10 is fully opened, and the pipeline returns to normal.

[0089] refer to Figure 1 and Figure 2The check valve of this application also includes a solenoid valve 4, a pressure source 5, an actuator 7, and a flow switch or flow meter 6. The solenoid valve 4 is a two-position five-way solenoid valve; the pressure source 5 is a cylinder or hydraulic bladder accumulator with instantaneous opening and closing function. The cylinder or hydraulic bladder accumulator provides an air or hydraulic source to drive the actuator 7 to move the gate 2 along the first direction Y. The cylinder or hydraulic bladder accumulator is connected to the two-position five-way solenoid valve. The two-position five-way solenoid valve 4 has a first solenoid coil 44, a second solenoid coil 45, an air inlet P, a first air outlet A, a second air outlet B, an exhaust port R, and an exhaust port S. The air inlet P is connected to the pressure source 5 through an air inlet pipe 41; the first air outlet A is connected to the first cavity 73 through a first exhaust pipe 42; the second air outlet B is connected to the second cavity 74 through a second exhaust pipe 43; the first exhaust pipe 42 is connected to the first air outlet A; and the second exhaust pipe 43 is connected to the second air outlet B. The first electromagnetic coil 44 controls the opening and closing of the first vent A to connect or disconnect the pressure source 5 from the first cavity 73. The second electromagnetic coil 45 controls the opening and closing of the second vent B to connect or disconnect the pressure source 5 from the second cavity 74. The first electromagnetic coil 44 of the four-way valve 4 is selectively connected to the flow meter 6 via a current switch 8. When the flow meter 6 detects that the flow rate in the pipe 100 is zero or close to zero, the flow meter 6 is connected to the electromagnetic valve 4 via the current switch 8, and the first electromagnetic coil 44 is energized to generate magnetic force, thereby opening the first vent A. The actuator 7 includes a housing 71 and a piston 72. The housing 71 is fixedly connected to the first body part 11 and the second body part 13 via a bracket. The piston 72 is disposed inside the housing 71 and divides the housing 71 into a first cavity 73 and a second cavity 74. The first exhaust pipe 42 is connected to the first cavity 73, and the second exhaust pipe 43 is connected to the second cavity 74. The main body part 21 of the gate 2 is connected to the side of the piston 72 away from the first cavity.

[0090] The check valve in this application is installed between two flanges at the outlet of a water pump in a pipeline water supply system. A flow switch or flow meter 6 is installed at the water pump outlet. The magnetic force of the second solenoid coil 45 of the two-position five-way solenoid valve 4 after being energized is greater than the magnetic force of the first solenoid coil 44 after being energized. The signal output line of the flow switch or flow meter 6 is connected to the two-position five-way solenoid valve 4 through a current switch 8. With this setup, when the water pump stops due to power failure and is restarted, the magnetic force generated by the second electromagnetic coil 45 after being re-energized is greater than that of the first electromagnetic coil 44 after being energized. The PA channel of the two-position five-way solenoid valve 4 gradually closes while the PB channel gradually opens. The gas or liquid in the pressure source 5 enters the second chamber 74 through the second exhaust pipe 43. The pressure of the gas or liquid in the second chamber 74 is greater than that of the gas or liquid entering the first chamber 73 through the first exhaust pipe 42. The pressure in the second chamber 74 is greater than that in the first chamber 73, which pushes the piston 72 to move the gate 2 in the first direction Y to open the fluid channel 10. When the reading of the flow switch or flow meter 6 is greater than zero, the current switch 8 cuts off the power to the first electromagnetic coil 44. The magnetic force of the first electromagnetic coil 44 completely disappears, the PA channel is completely closed while the PB channel is completely open, the check valve is fully reopened, and the system resumes normal water supply.

[0091] When the output flow rate or velocity of the flow switch or flow meter 6 is close to zero, the signal output line of the flow meter 6 connects the first electromagnetic coil 44 of the two-position five-way solenoid valve 4 through the current switch 8. After the first electromagnetic coil 44 is energized, it generates magnetic force, which connects the PA channel of the two-position five-way solenoid valve 4 and cuts off the PB channel. The air source or hydraulic source enters the first chamber 73 of the actuator 7 from the cylinder or hydraulic bladder accumulator through the first exhaust pipe 42. The pressure in the first chamber 73 is greater than the pressure in the second chamber 74, which pushes the piston 72 to drive the gate plate 2 to move quickly along the first direction Y, thereby blocking the fluid channel 10 and cutting off the water flow. This can reduce the additional water hammer added to the water pump, thereby effectively protecting the safety of the pipeline water supply system. When the check valve closes, the gate 2 moves perpendicular to the water flow direction in the first direction, and the valve closes instantaneously when the flow rate or velocity is close to zero. At the instant of valve closure, there is no disturbance to the water flow, or rather, the disturbance is negligible. In other words, the valve closure process neither changes the water flow direction nor the flow rate, therefore there is no change in flow velocity. Therefore, after the pump stops, the pipeline water supply system does not generate a second pressure-reducing water hammer. The system only has a first pressure-reducing water hammer generated when the pump stops. Therefore, the pressure-reducing water hammer generated by the check valve in this application is much smaller than that generated by the traditional check valve, which improves the safety and reliability of the pipeline water supply system. The water hammer protection measures adopted are simple and reduce costs.

[0092] Secondly, embodiments of this application provide a pipeline water supply system, including the check valve described in any of the above embodiments. The pipeline water supply system in this embodiment has the beneficial effects of the check valve described in any of the above embodiments.

[0093] For example, refer to Figure 6 Hydraulic model diagram of a pipeline water conveyance system equipped with the check valve 300 of this application or a conventional ordinary check valve 600.

[0094] The pipeline water supply system also includes a water pump 500, a water pump outlet manifold 900, a main pipe 800, a check valve 300, a water hammer elimination tank 700, and an air valve 400. The check valve 300 is connected to the main pipe 800. One end of the main pipe 800 is connected to four water pumps 500 arranged in parallel. Each water pump 500 has a check valve 300 at its outlet. The water hammer elimination tank 700 is installed on the water pump outlet manifold 900. The main pipe 800 has multiple air valves 400. Please refer to Table 1, which shows the specifications of the water pump 500 and the main pipe 800.

[0095]

[0096] Table 1

[0097] Please see Figure 7 , Figure 7 This is a steady-state hydraulic gradient diagram of a pipeline water conveyance system. Figure 7 The blue line represents the longitudinal profile of the main pipe (800), the green line represents the steady-state hydraulic gradient line, the X-axis represents the length of the main pipe (800), and the Y-axis represents the node elevation. The longitudinal profile refers to the curve projected onto the vertical plane from the centerline of the pipe. The steady-state hydraulic gradient line refers to the pressure head line during normal operation. The node elevation refers to the elevation (in meters) of a specific point on the pipe, representing the pressure value. From... Figure 7 As can be seen, when the four 500 water pumps work together, the steady-state flow rate is 902.9 L / s, and the highest pressure of the pipeline water supply system is approximately 219.5 m³ (the difference between the pressure value corresponding to the steady-state hydraulic gradient line and the pressure value corresponding to the longitudinal section line). The highest pressure occurs at the inlet of check valve 300. The water hammer control target is a maximum pressure increase of 219.5 × 1.5 = 329.25 m³. Therefore, the highest pressure resistance rating of the pipe material of main pipe 800 and various valves and other hydraulic machinery and materials in the pipeline water supply system is PN40, the minimum negative pressure must not be lower than -2 m³, and the speed of water pump 500 must not reverse.

[0098] Please see Figure 8 , Figure 8In case of pump failure and shutdown, a slow-closing hydraulic butterfly valve 600 from the traditional check valve category is selected as the backflow prevention device after the pump. A water hammer pressure envelope is constructed using a combination of an air valve and a water hammer elimination tank to protect against water hammer. In the diagram, the blue line represents the longitudinal section of the main pipe 800, the green line represents the steady-state pressure gradient line, and the rising and falling water hammer lines (red lines) represent the water hammer pressure envelope. The X-axis represents the pipeline length of the main pipe 800, and the Y-axis represents the node elevation. Figure 8 The display shows that most areas of the main pipe 800 have severe negative pressure, with the negative pressure as low as -8m and the highest pressure of 277m. This occurs at the outlet of the slow-closing hydraulic butterfly valve 600. The pressure reduction water hammer does not meet the water hammer control target, while the pressure increase water hammer does meet the water hammer control target.

[0099] Please see Figure 9 , Figure 9 In case of pump failure and shutdown, a silent check valve 600 from the traditional check valve system is selected as the backflow prevention device after the pump. A water hammer pressure envelope is constructed using a combination of an air valve and a water hammer elimination tank to protect against water hammer. In the diagram, the blue line represents the longitudinal section of the main pipe 800, the green line represents the steady-state pressure gradient line, and the rising and falling water hammer lines (red lines) represent the water hammer pressure envelope. The X-axis represents the pipeline length of the main pipe 800, and the Y-axis represents the node elevation. Figure 9 The main valve 800 shows severe negative pressure in most areas, with the negative pressure as low as -7.7m and the highest pressure of 249m, which occurs at the outlet of the silencer check valve 600. The pressure reduction water hammer does not meet the water hammer control target, while the pressure increase water hammer does meet the water hammer control target.

[0100] Please see Figure 10 , Figure 10 In the event of a pump failure and shutdown, the present invention, namely a zero-flow-rate, interference-free check valve 300, is selected as a backflow prevention device after the pump. This device employs a combination of an air valve and a water hammer elimination tank to protect against water hammer. The figure shows the longitudinal section of the main pipe 800, the steady-state pressure gradient line, the rising and falling water hammer lines (red lines) as the water hammer pressure envelope, the X-axis as the pipeline length of the main pipe 800, and the Y-axis as the node elevation. Figure 10 The indicator shows that the negative pressure of the main pipe 800 is very weak throughout, with the lowest negative pressure being only -0.3m and the highest pressure being 245m. The outlet of the check valve 300 of this application appears. Both the pressure-reducing water hammer and the pressure-increasing water hammer meet the water hammer control target.

[0101] Please see Figure 11 , Figure 11 This diagram illustrates the operation of a water pump 500 in a pipeline water supply system in which the check valve 300 of this application is installed. Figure 11 The display shows that the rotational speed of water pump 500 is not negative, indicating that water pump 500 has not reversed.

[0102] The check valve 300 provided by this invention can quickly and effectively eliminate negative pressure water hammer and pressure rise water hammer, ensuring the safe and reliable operation of the pipeline water conveyance system, and has a simple structure.

[0103] It should also be noted that 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 limitation, 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.

[0104] The various embodiments in this specification are described in a progressive manner. Similar or identical parts between embodiments can be referred to interchangeably. Each embodiment focuses on describing the differences from other embodiments. In particular, the system embodiments are basically similar to the method embodiments, so the description is relatively simple; relevant parts can be referred to the descriptions in the method embodiments.

[0105] The above description is merely an embodiment of this application and is not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principle of this application should be included within the scope of the claims of this application.

[0106] Although embodiments of this application have been described in conjunction with the accompanying drawings, those skilled in the art can make various modifications and variations without departing from the spirit and scope of this application, and such modifications and variations all fall within the scope defined by the appended claims.

Claims

1. A check valve, disposed in a pipeline (100), characterized in that, include: The valve body (1) has a fluid passage (10) along its axial direction (X). A flow meter (6) is installed in the pipe (100) and located between the water pump and the valve body (1) to detect the fluid flow rate in the pipe (100); A drive mechanism is provided in the valve body (1) and is selectively electrically connected to the flow meter (6); A gate (2) is connected to the drive end of the drive mechanism. Along the first direction (Y), the gate (2) moves relative to the valve body (1) and has a first position and a second position. The drive mechanism drives the gate (2) to move between the first position and the second position. When the gate (2) is in the first position, the gate (2) is located outside the fluid channel (10). When the gate (2) is in the second position, the gate (2) is inserted into the fluid channel (10) and blocks the fluid channel (10). The first direction (Y) is perpendicular to the axial direction (X) of the valve body (1). After the pump stops, when the flow meter (6) detects that the flow rate in the pipe (100) is zero or close to zero, the flow meter (6) is electrically connected to the drive mechanism. The drive mechanism controls the gate (2) to move from the first position toward the second position to block the fluid channel (10).

2. The check valve according to claim 1, characterized in that, The valve body (1) includes a first valve body and a second valve body. The fluid channel (10) includes a first fluid channel and a second fluid channel. The first valve body also includes a first body part (11) and a first valve seat (12). The first valve seat (12) surrounds the first fluid channel (10). The first body part (11) is sleeved on the outside of the first valve seat (12). The second valve body also includes a second body part (13) and a second valve seat (14). The second valve seat (14) surrounds the second fluid channel (10). The second body part (13) is sleeved on the outside of the second valve seat (14). When the gate (2) is in the first position, the first valve seat (12) and the second valve seat (14) abut against each other along the axial direction (X) of the valve body (1). When the gate (2) is in the second position, the gate (2) squeezes the first valve seat (12) and the second valve seat (14) along the axial direction (X) of the valve body (1) to extend between the first fluid channel (10) and the second fluid channel (10).

3. The check valve according to claim 2, characterized in that, Both the first valve seat (12) and the second valve seat (14) are constructed as elastic elements.

4. The check valve according to claim 2, characterized in that, The first valve seat (12) and the second valve seat (14) have a first end (121) and a second end (141) facing each other, respectively. When the gate (2) is in the first position, the outer periphery of the first end (121) and the outer periphery of the second end (141) form a first guide groove (15). The cross-sectional area of ​​the first guide groove (15) gradually increases along the radial direction of the valve body (1). When the gate (2) is in the first position, the inner circumference of the first end (121) and the inner circumference of the second end (141) form a second guide groove (16), and the cross-sectional area of ​​the second guide groove (16) gradually decreases along the radial direction of the valve body (1).

5. The check valve according to claim 4, characterized in that, The first valve seat (12) includes a first segment (122) and a second segment (123), and the second valve seat (14) includes a third segment (142) and a fourth segment (143) connected together. Along the axial direction (X) of the valve body (1), the first segment (122) is connected to the second segment (123), and the third segment (142) is connected to the fourth segment (143). When the gate (2) is in the first position, the second segment (123) abuts against the third segment (142). Along the radial direction of the valve body (1), the thickness of the first segment (122) is less than the thickness of the second segment (123), and the thickness of the fourth segment (143) is less than the thickness of the third segment (142).

6. The check valve according to claim 5, characterized in that, From the first segment (122) to the second segment (123), the thickness of the first segment (122) gradually increases in the radial direction of the valve body (1); from the fourth segment (143) to the third segment (142), the thickness of the fourth segment (143) gradually increases in the radial direction of the valve body (1).

7. The check valve according to claim 1, characterized in that, Along the first direction (Y), the gate (2) includes a connected main body (21) and a first guide (22), and the cross-sectional area of ​​the first guide (22) gradually decreases along the first direction (Y) from the main body (21) to the first guide (22).

8. The check valve according to claim 1, characterized in that, The flow meter (6) has a detection unit (61) located in the pipe (100) for detecting the fluid flow rate in the pipe (100).

9. The check valve according to claim 1, characterized in that, The drive mechanism includes: A power assembly, which is electrically connected to the flow meter (6). An actuator (7) is connected to the power assembly and the gate (2) to drive the gate (2) to move between the first position and the second position.

10. The check valve according to claim 9, characterized in that, The power assembly includes a pressure source (5) containing a medium; the drive mechanism further includes a solenoid valve (4) selectively electrically connected to the flow meter (6), the solenoid valve (4) having an inlet (P), a first outlet (A), and a second outlet (B), the inlet (P) being connected to the pressure source (5); wherein, The actuator (7) includes a housing (71) and a piston (72). The housing (71) is connected to the valve body (1). The piston (72) is located inside the housing (71) and divides the housing (71) into a first cavity (73) and a second cavity (74). The first vent (A) communicates with the first cavity (73), and the second vent (B) communicates with the second cavity (74). The piston (72) is connected to the gate (2) to drive the gate (2) to move between the first position and the second position.

11. A pipeline water conveyance system, characterized in that, Includes the check valve as described in any one of claims 1 to 10.

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