A swing check valve

Abstract

This invention discloses a swing check valve, specifically relating to the field of valve technology. It includes a valve body, valve cover, support component, pin shaft, rocker arm, valve disc, and limiting block, as well as a damping assembly. Through the damping assembly, this invention enables the drive plate to move a second piston while the valve disc is opening, forcing gas from the drive chamber into two driven chambers. This causes the two second mounting plates to move their corresponding friction blocks towards their corresponding first mounting plates, allowing the friction blocks to contact the first or second friction plates, generating a rotational damping effect. Furthermore, under high-flow pulsating conditions, this prevents the valve disc from directly overcoming frictional forces to deflect, avoiding repeated oscillations and extending valve life. Under low-flow pulsating conditions, it also slows the valve disc closing speed, preventing rapid closure of the valve disc's sealing surface and further extending valve life.

Description

Technical Field

[0001] This invention relates to the field of valve technology, and more specifically, to a swing check valve. Background Technology

[0002] A swing check valve is an industrial pipeline control device, mainly used to prevent backflow of media and ensure unidirectional flow of fluid. It is suitable for chemical, petroleum, power plant and other fields. Its working principle is based on the medium pressure driving the valve disc to swing around the rotation axis: the valve disc opens automatically when flowing in the direction of flow, and closes by its own weight and reverse force when flowing against the flow.

[0003] Chinese patent application CN202011020578.5 discloses a swing check valve, including a valve body with a valve cavity inside. The valve body has an inlet pipe and an outlet pipe communicating with the valve cavity on its side. A valve cover is fixedly installed at the upper opening of the valve cavity. The valve cavity is characterized by having two support rods above the inlet pipe on the left side wall above the valve cavity, with a horizontal shaft between the two support rods along an axial direction perpendicular to the inlet pipe. A bushing is rotatably connected to the shaft, and a rocker arm extends outward from the bushing. A valve disc for controlling the opening and closing of the inlet pipe is fixedly installed at the end of the rocker arm away from the support rods. A pressure block is slidably connected to the left side wall of the valve cavity below the support rods along the axial direction of the shaft. An elastic element for forcing the pressure block to move towards the rear side wall of the valve cavity is provided at one end of the pressure block on the front side wall of the valve cavity. A transmission assembly connected to the bushing is provided inside the pressure block. This swing check valve is not only structurally sound and reliable in use, but also allows for rapid opening and slow closing of the valve disc, and is shockproof.

[0004] Although the valve disc of the above invention can open quickly and close slowly and prevent impact, factors such as periodic fluctuations in flow velocity or pressure in the fluid delivery system can cause pulse flow during the fluid delivery process. The pulse flow can prevent the valve disc of the swing check valve from fully opening or stabilizing at a certain position, resulting in continuous oscillation of the swing check valve, which can damage the valve disc or valve body structure and affect the service life of the check valve.

[0005] This invention provides a swing check valve, which aims to solve the problem that pulse flow can prevent the valve disc of the swing check valve from fully opening or stabilizing at a certain position, resulting in continuous oscillation of the swing check valve, which can damage the valve disc or valve body structure and affect the service life of the check valve. Summary of the Invention

[0006] The purpose of this invention is to provide a swing check valve to solve the problem mentioned in the background art that the pulse flow causes the valve disc of the swing check valve to be unable to fully open or stabilize at a certain position, resulting in continuous oscillation of the swing check valve, which damages the valve disc or valve body structure and affects the service life of the check valve.

[0007] To achieve the above objectives, the present invention provides the following technical solution: a swing check valve, comprising a valve body, a valve cover, a support member, a pin shaft, a rocker arm, a valve disc, and a limiting block, and further comprising a damping assembly, wherein the damping assembly is used to provide adaptive damping force when the valve disc is opened or closed, so as to suppress valve disc oscillation caused by pulse flow.

[0008] Preferably, the damping component includes:

[0009] Two first mounting plates fixed at both ends of the pin shaft;

[0010] A first friction plate and a second friction plate are disposed on each of the first mounting plates;

[0011] Two driven chambers are symmetrically arranged in the valve body, and each of the two driven chambers is provided with a slidable first piston;

[0012] The support rods connected to the first piston are provided with a second mounting plate and a friction block at the end of each support rod, and an elastic element is sleeved on each support rod;

[0013] The driving chamber and the second piston that slides inside the driving chamber are connected to the two driven chambers through an output channel.

[0014] Preferably, the drive chamber is provided with a drive plate. When the medium flows, the drive plate is pushed to drive the second piston to compress the gas in the drive chamber. The gas enters the driven chamber through the output channel to push the corresponding first piston to move, so that the friction block contacts the first friction plate or the second friction plate to generate friction.

[0015] Preferably, the elastic element is disposed in the driven cavity and is used to push the first piston to reset when the medium flow rate decreases, so that the friction block gradually disengages from the first friction plate or the second friction plate to reduce the damping force.

[0016] Preferably, a gap is provided between the first friction plate and the second friction plate, so that when the valve disc moves in the middle position, the friction block does not contact the first friction plate or the second friction plate.

[0017] Preferably, the contact surface between the friction block and the first friction plate and the second friction plate is a wedge-shaped surface.

[0018] Preferably, the inner diameter of the drive plate is smaller than the inner diameter of the input end, for using lateral fluid pressure to drive the damping assembly.

[0019] Preferably, the second piston is fixedly connected to the drive plate via a support ring.

[0020] Preferably, the rocker arm is fixedly connected to the pin shaft to rotate around the lower rotating groove of the support member.

[0021] Preferably, the limiting block is used to limit the maximum opening angle of the valve disc.

[0022] The technical effects and advantages of this invention are as follows:

[0023] 1. This invention, through the setting of a damping component, can push the drive plate to drive the second piston while the valve disc is opening, squeezing the gas in the drive chamber into the two driven chambers. This causes the two second mounting plates to drive the corresponding friction blocks to move towards the corresponding first mounting plate, allowing the friction blocks to contact the first or second friction plate, generating a rotational damping effect. In the case of high-flow pulsating flow, this prevents the valve disc from directly overcoming frictional force to deflect, avoiding repeated oscillation of the valve disc and extending the valve life. In the case of low-flow pulsating flow, it can also slow down the valve disc closing speed, preventing the valve disc sealing surface from closing too quickly and causing damage, further extending the valve life. Furthermore, it can coordinate with the medium flow rate to prevent the valve disc from directly closing and blocking the medium flow, thereby reducing pressure loss and improving system energy efficiency. Attached Figure Description

[0024] Figure 1 This is a schematic diagram of the overall structure of the present invention.

[0025] Figure 2 This is a cross-sectional view of the overall internal structure of the present invention.

[0026] Figure 3 This is a partial cross-sectional view of the output channel portion of the present invention.

[0027] Figure 4 This is a schematic diagram of the structure of the second piston part of the present invention.

[0028] Figure 5 This is a cross-sectional view of the internal structure of the driven cavity portion of the present invention.

[0029] Figure 6 For the present invention Figure 5 Enlarged view of the structure of part A.

[0030] Figure 7 This is a schematic diagram of the valve disc portion of the present invention.

[0031] Figure 8 This is an exploded view of the valve disc structure of the present invention.

[0032] Figure 9 This is a schematic diagram of the structure of the second mounting plate portion of the present invention.

[0033] Figure 10 This is a schematic diagram of the structure of the first mounting plate portion of the present invention.

[0034] The attached figures are labeled as follows: 1. Valve body; 11. Input end; 12. Output end; 2. Valve cover; 3. Support member; 31. Pin shaft; 32. Rocker arm; 33. Valve disc; 34. Limiting block; 4. Damping assembly; 41. First mounting plate; 42. First friction plate; 43. Second friction plate; 44. Driven chamber; 45. First piston; 46. Support rod; 47. Second mounting plate; 48. Friction block; 49. Drive chamber; 410. Second piston; 411. Support ring; 412. Drive plate; 413. Output channel; 414. Elastic element. 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 actual use, existing swing check valves may experience pulse flow due to factors such as periodic fluctuations in flow velocity or pressure within the fluid delivery system. This pulse flow can prevent the valve disc from fully opening or stabilizing at a certain position, causing continuous oscillations in the swing check valve. This can damage the valve disc or valve body structure and affect the service life of the check valve.

[0037] refer to Figures 1 to 10 An embodiment of the present invention provides a swing check valve, comprising a valve body 1 and a valve cover 2. The valve body 1 has an input end 11 for medium input and an output end 12 for medium output at its two ends. A support member 3 is fixedly connected above the input end 11 inside the valve body 1. The lower part of the support member 3 is rotatably connected to a pin shaft 31 through a rotating groove. A rocker arm 32 is fixedly connected to the outer periphery of the pin shaft 31. A valve disc 33 for blocking the input end 11 is installed at the other end of the rocker arm 32. A limiting block 34 for limiting the rotation angle of the valve disc 33 is fixedly connected above the output end 12 inside the valve body 1.

[0038] refer to Figures 2 to 10 It also includes a damping assembly 4, which includes two first mounting plates 41 fixedly connected to both ends of the pin shaft 31. On the side of the two first mounting plates 41 that are far apart from each other, there are symmetrically arranged first friction plates 42 and second friction plates 43 fixedly connected.

[0039] refer to Figures 3 to 6The valve body 1 has two symmetrically arranged driven chambers 44, which are located at both ends of the pin shaft 31. Each driven chamber 44 is sealed and slidably connected to a first piston 45. Each of the two first pistons 45 is fixedly connected to a support rod 46 that extends to the outside of the driven chamber 44 on the side of the two first pistons 45 that is close to each other. The other end of each of the two support rods 46 is fixedly connected to a second mounting plate 47 that corresponds to the position of the two first mounting plates 41. Each of the two second mounting plates 47 is fixedly connected to a friction block 48 on the side of the two second mounting plates that is close to each other. Each of the two support rods 46 is fitted with an elastic element 414. One end of each elastic element 414 is connected to the corresponding first piston 45, and the other end is connected to the inner wall of the corresponding driven chamber 44.

[0040] refer to Figure 6 , Figure 9 and Figure 10 When the valve disc 33 is in the blocked state, the friction block 48 corresponds to the position of the first friction plate 42. When the valve disc 33 is in the open state, the friction block 48 corresponds to the position of the second friction plate 43. The contact surfaces of the first friction plate 42, the second friction plate 43 and the friction block 48 are all set as wedge-shaped surfaces that can cooperate with each other. The starting position of the limit can be adjusted synchronously by adjusting the size of the first friction plate 42, the second friction plate 43 and the friction block 48.

[0041] refer to Figures 2 to 4 The input end 11 has an annular drive cavity 49 inside. The end of the drive cavity 49 away from the valve disc 33 is connected to the inner side of the input end 11. The drive cavity 49 is sealed and slidably connected to a second piston 410. The side of the second piston 410 away from the valve disc 33 is fixedly connected to a support ring 411. The other end of the support ring 411 is fixedly connected to a drive plate 412 located inside the input end 11. The inner diameter of the drive plate 412 is smaller than the inner diameter of the input end 11. The valve body 1 has two output channels 413 inside. The drive cavity 49 can be connected to two driven cavities 44 through the two output channels 413 respectively.

[0042] In actual operation, the input end 11 and output end 12 of the swing check valve are connected to the pipeline. When the medium in the pipeline flows in through the input end 11, the medium will push the valve disc 33 to rotate around the rotating groove on the support 3 under the action of the rocker arm 32 and the pin shaft 31, opening the blockage on the input end 11, so that the medium can flow out through the output end 12.

[0043] As the medium flows into the input end 11, it pushes the drive plate 412 to move toward the valve disc 33. During the movement, the support ring 411 pushes the second piston 410 to move in the drive chamber 49, squeezing the gas in the drive chamber 49 into the two driven chambers 44 through the two output channels 413. The gas entering the two driven chambers 44 pushes the two first pistons 45 to move in the corresponding driven chambers 44 and compresses the elastic element 414. The two first pistons 45 drive the two second mounting plates 47 to move through the corresponding support rods 46, so that the two second mounting plates 47 drive the corresponding friction blocks 48 to move toward the corresponding first mounting plates 41, so that the friction blocks 48 can contact the first friction plate 42 or the second friction plate 43, producing a rotational damping effect.

[0044] Since the gas in the drive chamber 49 needs to pass through the output channel 413 to enter the driven chamber 44, it takes a certain amount of time for the gas to flow into the driven chamber 44. This causes a certain time delay in the movement of the first piston 45, which drives the second mounting plate 47 and the friction block 48. As a result, the friction block 48 will not contact the first friction plate 42 when the valve disc 33 is opened, and will not have a damping effect on the opening of the valve disc 33, so that the valve disc 33 can open normally and quickly.

[0045] The speed at which the gas enters the driven chamber 44 can be adjusted synchronously by adjusting the diameter of the output channel 413 or the inner diameter of the drive plate 412 according to the actual working conditions, which can adjust the timing of the full extension of the friction block 48.

[0046] refer to Figure 9 and Figure 10 A certain gap is reserved between the first friction plate 42 and the second friction plate 43, so that when the valve disc 33 is opened, the friction block 48 can move into the gap between the first friction plate 42 and the second friction plate 43. The friction block 48 will not have a damping effect on the opening of the valve disc 33 while it is in the gap, thus avoiding unnecessary energy consumption. When the valve disc 33 is about to contact the limiting block 34 and fully open, the position of the friction block 48 corresponds to that of the second friction plate 43. The second friction plate 43 can squeeze the friction block 48 through the wedge-shaped surface cooperation between it and the friction block 48, so that the surface of the second friction plate 43 can contact the surface of the friction block 48, thus producing a damping effect and preventing the valve disc 33 from impacting the limiting block 34.

[0047] Meanwhile, the greater the flow rate in the pipeline, the greater the force of the medium pushing the drive plate 412, resulting in more gas entering the driven chamber 44, pushing the friction block 48 to move a greater distance, and thus providing greater damping friction. This allows the damping friction to be adaptively adjusted according to the flow rate of the medium. On the one hand, it can prevent the friction from being too small when the flow rate is too large, which would cause an impact between the valve disc 33 and the limit block 34, reducing mechanical wear and noise and extending the valve life. On the other hand, it can prevent the friction from being too large when the flow rate is small, which would prevent the valve disc 33 from being fully opened, thereby reducing pressure loss and improving system energy efficiency.

[0048] When a large-flow pulsating flow occurs, causing a sudden decrease in the medium flow rate, the medium still provides a large thrust to push the drive plate 412, causing the gas in the drive chamber 49 to enter the driven chamber 44, and the friction block 48 to be in the extended state. At this time, the damping component 4 can still play a friction damping role, and the medium is still in a flowing state and cannot flow back through the output end 12. At this time, the valve disc 33 cannot directly overcome the friction force to deflect by its own weight. After the medium flow rate is quickly restored, there will be no impact between the valve disc 33 and the limit block 34, thereby avoiding repeated oscillation of the valve disc 33 and extending the valve life.

[0049] When a small flow pulsation occurs, the medium flow rate will suddenly decrease or be interrupted. When the flow rate decreases, the medium can provide some thrust to the drive plate 412. The elastic element 414 will push the first piston 45 to squeeze some gas in the driven chamber 44 into the drive chamber 49 through the output channel 413, which will reduce the friction provided by the friction block 48. At this time, the medium is still in a flowing state and cannot be returned through the output end 12. At this time, the valve disc 33 can gradually overcome the friction between the friction block 48 and the second friction plate 43 by its own weight and rotate. During the rotation of the valve disc 33, it will drive the pin shaft 31 and the first mounting plate 41 to rotate. When the first mounting plate 41 rotates and drives the first friction plate 42 to contact the friction block 48, a certain friction can be continuously generated between the first friction plate 42 and the friction block 48, which can slow down the closing speed of the valve disc 33 and prevent the valve disc 33 from directly closing and blocking the flow of the medium in coordination with the medium flow rate, thereby further improving the system energy efficiency.

[0050] When the flow is interrupted, the elastic element 414 will push the first piston 45 to gradually squeeze the gas in the driven chamber 44 into the drive chamber 49 through the output channel 413. Since the gas flow takes a certain amount of time, after the medium flow is interrupted, the friction block 48 will take a certain amount of time to return to the initial position. The valve disc 33 will rotate rapidly under its own weight and the backflow of the medium. During the rotation of the valve disc 33, it will drive the pin shaft 31 and the first mounting plate 41 to rotate. When the first mounting plate 41 rotates, it will drive the first friction plate 42 to contact the friction block 48. At this time, the friction block 48 can still play a damping role for the closing of the valve disc 33, slow down the closing time of the valve disc 33, avoid damage caused by the rapid closing of the sealing surface of the valve disc 33, and further extend the service life of the valve.

[0051] In summary, by setting up the damping component 4, the drive plate 412 can be pushed to drive the second piston 410 to squeeze the gas in the drive chamber 49 into the two driven chambers 44 when the valve disc 33 opens. This causes the two second mounting plates 47 to drive the corresponding friction blocks 48 to move towards the corresponding first mounting plate 41, so that the friction blocks 48 can contact the first friction plate 42 or the second friction plate 43, producing a rotational damping effect. In the case of large flow pulsating flow, the valve disc 33 cannot directly overcome the friction force to deflect, avoiding repeated oscillation of the valve disc 33 and extending the valve life. In the case of small flow pulsating flow, the closing speed of the valve disc 33 can be slowed down, avoiding rapid closure of the sealing surface of the valve disc 33 and causing damage, further extending the valve life. It can also be matched with the medium flow to prevent the valve disc 33 from directly closing and blocking the medium flow, thereby reducing pressure loss and improving system energy efficiency.

[0052] In conclusion, the above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A swing check valve, comprising a valve body (1), a valve cover (2), a support member (3), a pin shaft (31), a rocker arm (32), a valve disc (33), and a limiting block (34), characterized in that: It also includes a damping component (4) for providing an adaptive damping force when the valve disc (33) is opened or closed to suppress valve disc oscillation caused by pulse flow; The damping component (4) includes: Two first mounting plates (41) are fixed at both ends of the pin shaft (31); A first friction plate (42) and a second friction plate (43) are provided on each of the first mounting plates (41); Two driven chambers (44) are symmetrically arranged in the valve body (1), and each of the two driven chambers (44) is provided with a sliding first piston (45). The support rod (46) connected to the first piston (45) is provided with a second mounting plate (47) and a friction block (48) at the end of each support rod (46), and an elastic element (414) is sleeved on each support rod (46). The driving cavity (49) and the second piston (410) sliding inside the driving cavity (49) are connected to the two driven cavities (44) through the output channel (413); The drive chamber (49) is provided with a drive plate (412). When the medium flows, the drive plate (412) is pushed to drive the second piston (410) to compress the gas in the drive chamber (49). The gas enters the driven chamber (44) through the output channel (413) to push the corresponding first piston (45) to move, so that the friction block (48) contacts the first friction plate (42) or the second friction plate (43) to generate friction.

2. The swing check valve according to claim 1, characterized in that: The elastic element (414) is located in the driven cavity (44) and is used to push the first piston (45) to reset when the medium flow rate decreases, so that the friction block (48) gradually disengages from the first friction plate (42) or the second friction plate (43) to reduce the damping force.

3. The swing check valve according to claim 2, characterized in that: A gap is provided between the first friction plate (42) and the second friction plate (43) so that when the valve disc (33) moves in the middle position, the friction block (48) does not contact the first friction plate (42) or the second friction plate (43).

4. The swing check valve according to claim 3, characterized in that: The contact surface between the friction block (48) and the first friction plate (42) and the second friction plate (43) is a wedge-shaped surface.

5. The swing check valve according to claim 4, characterized in that: The inner diameter of the drive plate (412) is smaller than the inner diameter of the input end (11) for driving the damping assembly (4) using lateral fluid pressure.

6. The swing check valve according to claim 5, characterized in that: The second piston (410) is fixedly connected to the drive plate (412) via a support ring (411).

7. The swing check valve according to claim 6, characterized in that: The rocker arm (32) is fixedly connected to the pin shaft (31) to rotate around the lower groove of the support member (3).

8. The swing check valve according to claim 7, characterized in that: The limiting block (34) is used to limit the maximum opening angle of the valve disc (33).

Images