A type of air valve

Abstract

This application discloses a damper, comprising a valve body, a valve core, and a drive mechanism. The valve body has a cylindrical shell, and the valve core includes: at least two support rods and a central shaft. The central shaft is axially arranged along the centerline of the shell, and each support rod is radially arranged along the shell, with one end fixedly connected to the central shaft and the other end fixedly connected to the shell; multiple annular blades, including at least two hidden support rod blades, each corresponding to one support rod. The hidden support rod blades have hollow sleeves along their rotation axis, and each hidden support rod blade is fitted onto a support rod through its hollow sleeve and can rotate around the support rod. By completely concealing the support rods inside the blades of the valve core, this application can reduce wind resistance and shorten the axial length of the valve body.

Description

Technical Field

[0001] This application relates to the field of gas flow control, and more particularly to a damper. Background Technology

[0002] As a key regulating device in gas pipeline systems, air valves are widely used in fields such as fossil chemical industry, energy and environmental protection, building materials and metallurgy, food and medicine, and municipal construction.

[0003] A valve core is required in the air duct of a damper to control gas flow. Patent document CN107289170B discloses a damper with multiple reinforcing ribs (or support rods) at the bottom of the valve body cavity, originating from the inner wall and intersecting the valve body's central axis. A fixing part for securing a gearbox is located axially at the center of the reinforcing ribs, where multiple blades controlling gas flow are connected to a central gear within the gearbox via gears. While this design secures the gearbox, the reinforcing ribs in the air duct obstruct airflow, increasing wind resistance. Furthermore, to provide sufficient space for the reinforcing ribs, the axial length of the valve body needs to be increased, resulting in a larger damper size. Utility Model Content

[0004] To address the aforementioned technical problems, the purpose of this application is to provide a wind valve with a concealed support rod structure, thereby reducing the impact on the airflow passing through the valve body and also reducing the axial length of the valve body and the volume of the wind valve.

[0005] This application provides a damper, including a valve body, a valve core, and a drive mechanism. The valve body has a cylindrical shell. The valve core includes: a support structure comprising at least two support rods and a central shaft. The central shaft is axially arranged along the centerline of the shell. Each support rod is radially arranged along the shell, with one end fixedly connected to the central shaft and the other end fixedly connected to the shell. The connection points of the at least two support rods and the central shaft are located at the same height on the central shaft. A first central gear and a second central gear are sleeved on the central shaft and rotatable around the central shaft. Both the first central gear and the second central gear are bevel gears. The first central gear and the second central gear are respectively arranged on both sides of the connection points of the support rods and the central shaft, and the teeth of the first central gear and the second central gear are arranged opposite to each other. A plurality of fan-shaped blades are provided, and each blade has a blade gear fixedly arranged on its inner edge. The blade gear is rotatable. The blade's rotation axis is a bevel gear that rotates, and the rotation axis of the blade is parallel to the radial direction of the blade. Each blade gear is disposed between the first central gear and the second central gear and meshes with the two central gears. The plurality of blades includes a drive blade and at least two support rod hidden blades. Each support rod hidden blade corresponds to a support rod. The support rod hidden blade has a hollow sleeve along its rotation axis. Each support rod hidden blade is sleeved on the support rod through its hollow sleeve and can rotate around the support rod. The outer edge of the drive blade has a drive end connected to the drive mechanism. The drive mechanism applies torque to the drive end of the drive blade to make the drive blade rotate around its rotation axis, driving the first central gear and the second central gear to rotate, thereby driving the other blades to rotate around their respective rotation axes, so as to change the opening of the valve core and thereby regulate the gas flow rate through the valve body.

[0006] In some embodiments, the support rod is integrally formed with the central shaft.

[0007] In other embodiments, the support rod is detachably connected to the central shaft.

[0008] In the above embodiment, the central shaft has a connection hole at the connection point with the support rod, and the support rod is detachably connected to the central shaft through the connection hole.

[0009] In some embodiments, the number of support rods is three or more.

[0010] In some embodiments, each blade is an axisymmetric structure with its rotation axis as the axis of symmetry.

[0011] In some embodiments, the drive end is detachably connected to the outer edge of the drive blade.

[0012] In some embodiments, the thickness of each blade gradually decreases on both sides along its rotational axis.

[0013] In some embodiments, a first cavity and a second cavity that are not interconnected are provided between the inner wall and the outer wall of the housing. The inner wall of the housing is provided with a first opening communicating with the first cavity and a second opening communicating with the second cavity. The height of the first opening relative to the outer wall of the housing is greater than the height of the second opening relative to the outer wall of the housing. The air valve also includes a differential pressure sensor, which is in fluid communication with the first cavity and the second cavity of the valve body, and is used to measure the pressure difference between the first cavity and the second cavity.

[0014] In the above embodiments, the drive mechanism includes: a controller configured to generate a flow control signal based on the pressure difference measured by the differential pressure sensor; and a drive motor configured to apply torque to the drive end of the drive blade according to the flow control signal to rotate the drive blade by a corresponding angle.

[0015] The valve core of this application, by completely concealing the support rod inside the blade, has the following beneficial effects: reducing the impact on airflow, reducing wind resistance, reducing the axial length of the valve body, and reducing the volume of the valve. Attached Figure Description

[0016] Figure 1 An air valve 1 according to an embodiment of this application is shown;

[0017] Figure 2 It shows that Figure 1 A schematic diagram of the valve core 30 after the stroke valve 1 has been removed;

[0018] Figure 3 It shows Figure 2 View of the gas inflow side of the middle valve body 10;

[0019] Figure 4 It shows Figure 2 A schematic diagram of the structure of the annular guide surface 120 in the middle;

[0020] Figure 5 It shows from another perspective Figure 4 The structure of the annular guide surface 120;

[0021] Figure 6 It shows Figure 4 and Figure 5 Side view of the annular guide surface 120;

[0022] Figure 7 It shows along Figure 2 A cross-sectional view along the AA direction;

[0023] Figure 8 A side sectional view of a damper 1 according to an embodiment of this application is shown;

[0024] Figure 9 An assembly schematic diagram of the valve core 30 according to an embodiment of this application is shown;

[0025] Figure 10 It shows Figure 9 Side view of valve core 30. Detailed Implementation

[0026] The present application will now be described in detail with reference to specific embodiments. These embodiments will help those skilled in the art to further understand the present application, but are not intended to limit the present application in any way. It should be noted that those skilled in the art can make several modifications and improvements without departing from the concept of the present application. These all fall within the protection scope of the present application.

[0027] Figure 1 An embodiment of a damper 1 according to this application is shown. The damper 1 includes a valve body 10, a differential pressure sensor (not shown), a valve core 30, and a drive mechanism (not shown). For ease of understanding, Figure 2 The text shows that... Figure 1 A schematic diagram of the valve core 30 after the stroke valve 1 has been removed.

[0028] like Figure 2 As shown, the valve body 10 has a cylindrical shell 11, and the inner wall of the shell 11 includes an annular guide surface 120. When the air valve 1 is in the open state, gas flows in from the air inlet 128 of the shell 11, flows through the annular guide surface 120, and flows out from the air outlet 129 of the shell 11. Figure 2 Ray BC in the diagram indicates the direction of gas flow. It should be noted that... Figures 1-2 In the illustrated embodiment, the valve core 30 is installed downstream of the annular guide surface 120 of the valve body 10 (i.e., gas flows from the annular guide surface 120 to the valve core 30). However, those skilled in the art will understand that the valve core 30 can also be installed upstream of the annular guide surface 120 (i.e., gas flows from the valve core 30 to the annular guide surface 120). This application does not impose any limitation on the relative positional relationship between the valve core 30 and the annular guide surface 120.

[0029] Figure 3 It shows Figure 2 View of the gas inflow side of the middle valve body 10. Figure 4 It shows Figure 2 A schematic diagram of the structure of the annular guide surface 120. Figure 5 It shows from another perspective Figure 4 The structure of the annular guide surface 120. Figure 6 It shows Figure 4 and Figure 5 Side view of the annular guide surface 120.

[0030] like Figures 3 to 5 As shown, the annular guide surface 120 includes a plurality of raised surfaces 121 arranged along its circumference. Each raised surface 121 has a ridge line 122 along the gas flow direction. A valley 123 is formed between two adjacent raised surfaces 121. The valley line (not shown in the figure) between two adjacent raised surfaces 121 is the boundary line between the two adjacent raised surfaces 121.

[0031] In this application, the raised surface 121 is a surface that is raised in the middle relative to the periphery, and can be figuratively understood as a surface similar to the shape of a shark fin.

[0032] In some embodiments, each raised surface 121 is symmetrical about its ridgeline 122 along the circumferential direction of the annular guide surface 120. The radial projections of the ridgeline and valley line onto the housing 11 are parallel to the central axis of the housing 11. Here, the radial projection of the geometry on the raised surface 121 represents the pattern formed on the inner surface of the housing after light rays emitted radially from the central axis of the annular guide surface 120 are blocked by the shape. In this application, for ease of describing the shape of the surface, each raised surface 121 is regarded as a mountain, using relevant concepts from geography. In this application, a ridge refers to a raised strip-shaped ridge structure formed by the intersection of two slopes with opposite directions on both sides of the raised surface 121 along the circumferential direction, and the line connecting its highest points is called the ridgeline. The region between the ridges of two adjacent raised surfaces 121 is called a valley.

[0033] This structure allows the valley to function as a flow channel, guiding the gas in and reducing wind resistance, turbulence, vibration, and noise. In some embodiments, the annular flow guide surface 120 is a smooth surface, which further helps reduce wind resistance.

[0034] Figure 7 It shows along Figure 2 A cross-sectional view along the AA direction.

[0035] like Figures 3-7As shown, the annular guide surface 120 and the outer wall of the housing 11 are separated by an annular separator 124 into a first cavity 125 and a second cavity 126 that are not interconnected. At least one raised surface 121 is provided with a first opening 125a communicating with the first cavity 125 and a second opening 126a communicating with the second cavity 126. The first opening 125a is located on the at least one raised surface 121 at a height of a first height h1 relative to the outer wall of the housing 11, and the second opening 126a is located on the at least one raised surface 121 at a height of a second height h2 relative to the outer wall of the housing 11. The first height h1 is greater than the second height h2. The distance from the first opening 125a to the air inlet 128 is greater than the distance from the second opening 126a to the air inlet 128. In this application, the height of a point on the raised surface 121 relative to the outer wall of the housing 11 refers to the radial distance from that point to the outer wall of the housing 11.

[0036] Because the first opening 125a and the second opening 126a are at different heights relative to the shell 11, the cross-sectional areas of the inner cavities of the shell 11 corresponding to the first opening 125a and the second opening 126a are different. When the gas flows through the annular guide surface 120, the flow velocities corresponding to the first opening 125a and the second opening 126a are different. According to Bernoulli's principle, the gas pressures of the first cavity 125 connected to the first opening 125a and the second cavity 126 connected to the second opening 126a are different. Therefore, there is a pressure difference between the first cavity 125 and the second cavity 126. Based on the pressure difference between the first cavity 125 and the second cavity 126, and the cross-sectional areas at the first opening 125a and the second opening 126a, the gas flow rate can be calculated using Bernoulli's equation.

[0037]

[0038] Where Q is the airflow volumetric flow rate (m³ / s) 3 / s), A1 is the cross-sectional area (m²) at the larger cross-section. 2 This refers to the cross-sectional area of ​​the inner cavity of the shell 11 at the second opening 126a, where A2 is the cross-sectional area at the smaller cross-section (m²). 2 This refers to the cross-sectional area of ​​the inner cavity of the shell 11 at the first opening 125a, A2 / A1 is the cross-sectional area shrinkage ratio, ΔP is the gas pressure difference between the first cavity 125 and the second cavity 126, and ρ is the gas density (kg / m³). 3 C is the flow coefficient, used to correct for frictional losses caused by fluid viscosity.

[0039] A differential pressure sensor (not shown in the figure) is used to measure the pressure difference between the first chamber 125 and the second chamber 126. It has a measuring circuit and two pressure input terminals. The two pressure input terminals are fluidly connected to the first chamber 125 and the second chamber 126 of the valve body 10, respectively. The measuring circuit converts the pressure difference between the two pressure input terminals into an electrical signal.

[0040] It should be noted that, in the foregoing embodiments, the first cavity 125 and the second cavity 126 can be disposed between the annular guide surface 120 and the housing 11, thus making full use of the space between the annular guide surface 120 and the outer wall of the housing 11. However, in other embodiments, the first cavity 125 and / or the second cavity 126 can be disposed at other locations between the inner and outer walls of the housing 11, as long as the first cavity 125 can connect to the first opening 125a and the second cavity 126 can connect to the second opening 126a, the corresponding functions can be achieved.

[0041] In some embodiments, the raised curved surface 121 is provided with a plurality of first openings 125a and a plurality of second openings 126a. Since the plurality of first openings 125a are all located at a first height and are all connected to the first cavity 125, and the plurality of second openings 126a are all located at a second height and are all connected to the second cavity 126, the pressure difference can be calculated using their average pressure value, which is beneficial to further reduce the deviation caused by airflow fluctuations and improve the stability of the measured data.

[0042] In some embodiments, to obtain a larger pressure difference and improve the accuracy of airflow measurement, the first opening 125a is located at the point of maximum height relative to the outer wall of the housing 11 on the inner wall, such as the peak point 127a of a plurality of raised surfaces, and the second opening 126a is located at the point of minimum height relative to the outer wall of the housing 11 on the inner wall, such as the lowest point of a plurality of raised surfaces, for example, near the end of the air inlet 128. With this arrangement, the maximum pressure difference between two different cross-sections of the inner cavity of the housing 11 can be measured, thereby improving the accuracy of gas flow measurement. Preferably, the plurality of raised surfaces have the same surface shape, and the first opening 125a is located at the peak point of each raised surface, and the second opening is located at the lowest point of each raised surface.

[0043] In some embodiments, the plurality of raised surfaces 121 include a first raised surface 121a and a second raised surface 121b, and the first raised surface 121a and the second raised surface 121b are alternately arranged in the circumferential direction. The height of the peak point 127a of the first raised surface 121a relative to the housing 11 is greater than the height of the peak point 127b of the second raised surface 121b relative to the housing 11, and the first opening 125a is provided at the peak point of each first raised surface 121a. This structure, with its alternating high and low surfaces, provides a larger airflow passage area compared to a case with multiple raised surfaces having the same surface shape and the first opening 125a being provided at the peak point of each raised surface, further reducing wind resistance. On the other hand, since the number of first openings 125a is equal to the number of first raised surfaces 121a, a better average value of the air pressure at the height of the peak point of the first raised surface 121a can be obtained. Therefore, this scheme can balance measurement accuracy and wind resistance.

[0044] In some embodiments, further, to balance measurement accuracy and wind resistance, the relative lengths of the arc lengths of the first raised surface 121a along the circumferential direction of the outer wall of the housing 11 and the arc lengths of the second raised surface 121b along the circumferential direction of the outer wall of the housing 11 can be adjusted. In this application, the arc length of the raised surface 121a along the circumferential direction of the outer wall of the housing 11 refers to the arc length of the radial projection of the valley line between the raised surface 121a and its adjacent raised surface along the circumferential direction of the outer wall of the housing 11. Figure 3 As shown, point O is the centerline position of the shell 11. The radial projection of the valley line between the first convex surface 121a and its adjacent convex surface along the circumferential direction of the outer wall of the shell 11 has an arc length of S1. The radial projection of the valley line between the other convex surface and its adjacent convex surface along the circumferential direction of the outer wall of the shell 11 has an arc length of S2. It can be understood that the larger the width ratio of the first convex surface 121a, the larger the cross-sectional area contraction ratio, and the larger the actual measured pressure difference. However, as the cross-sectional area contraction ratio increases, the drag coefficient also increases. As a compromise, the ratio of the arc length S1 of each first convex surface 121a along the circumferential direction of the outer wall of the shell 11 to the arc length S2 of each second convex surface 121b along the circumferential direction of the outer wall of the shell 11 can be set to 1.5-4 times.

[0045] In some embodiments, the ridgeline 122 of each raised surface 121 is monotonically increased in height relative to the housing 11 from the end near the air inlet 128 to the peak 127 of the raised surface 121, and monotonically decreased from the peak 121 to the end away from the air inlet 128. This allows the gas to flow smoothly over the annular guide surface, reducing turbulence and noise.

[0046] In some embodiments, the distance between the peak point 127 of each raised surface 121 and the side of the raised surface 121 near the air inlet 128 is greater than the distance between the peak point 127 and the side of the raised surface 121 near the air outlet 129. That is, a larger proportion of the axial length of the annular guide surface 120 is allocated to the gas rise slope, making the rise slope longer and gentler, resulting in a more uniform fluid velocity distribution, reducing boundary layer separation and eddy generation caused by sudden changes in flow velocity, and also reducing wear or noise caused by local high speeds.

[0047] Figure 8 A side sectional view of a damper 1 according to an embodiment of this application is shown. Figure 9 A schematic diagram of the assembly of a valve core 30 according to one embodiment of this application is shown. The valve core 30 is connected to the housing 11 and regulates the gas flow rate through the inner cavity of the valve body 10 under the control of a drive mechanism. The drive mechanism is configured to determine the adjustment amount of the valve core 30 based on the pressure difference measured by a differential pressure sensor and control the valve core 30 to perform the adjustment amount. In some embodiments, the differential pressure sensor and the drive mechanism are partially or entirely disposed outside the housing 11; in other embodiments, the differential pressure sensor and the drive mechanism can be integrated into an external module for easy maintenance and replacement.

[0048] like Figure 8 and Figure 9 As shown, the valve core 30 provided in this application includes a support structure 31, a central gear 32, and multiple annular blades 33.

[0049] The support structure 31 includes at least two support rods 311 and a central shaft 312. The central shaft 312 is axially arranged along the centerline 110 of the housing 11, and each support rod 311 is radially arranged along the housing 11. One end of each support rod 311 is fixedly connected to the central shaft 312, and the other end is fixedly connected to the housing 11 to fix the central shaft 312. The connection point 313 between the support rods 311 and the central shaft 312 is located at the same height as the central shaft 312.

[0050] In some embodiments, such as Figure 9 As shown, the central shaft 312 has a connecting hole at the connection point 313 with the support rod 311. The support rod 311 is detachably connected to the connecting hole of the central shaft 312, facilitating the installation and removal of the support rod 311. In some embodiments, the two support rods 311 can be a single unit, passing through the central shaft 312, for example... Figure 9 311b in the middle.

[0051] In some embodiments, the support rod 311 may also be fixedly connected to the central shaft 312 or integrally formed to improve stability.

[0052] In some embodiments, the number of support rods 311 is three or more, which are fixedly connected to the central shaft 312 at a certain angle, thereby providing a stable connection and support for the central shaft 312. Figure 9 In the embodiment shown, there are four support rods 311, including two integral support rods 311b that pass through the central shaft 312, and two support rods 311a that are connected to the central shaft 312 through the connecting holes at the connection point 313.

[0053] The central gear 32 includes a first central gear 321 and a second central gear 322, which are sleeved on the central shaft 312 and rotatable around the central shaft 312. Both the first central gear 321 and the second central gear 322 are bevel gears. The first central gear 321 and the second central gear 322 are respectively disposed on both sides of the connection point 313 between the support rod 311 and the central shaft 312, as shown below. Figure 9 The teeth of the first central gear 321 and the second central gear 322 are arranged opposite to each other on the upper and lower sides of the connection point 313 shown.

[0054] For ease of description, the side of the fan-shaped annular blade 33 closest to its center is called the inner side, the side furthest from its center is called the outer side, and the two sides along the radial direction are called the side edges. The outer edge of the blade 33 is an arc shape that mates with the inner wall of the housing 11, and the inner edge is a shape that mates with the outer side of the central gear. The inner edge of the blade 33 can be various shapes, such as arc or straight line, depending on the shape of the outer side of the gear. Each blade 33 has a fixed blade gear 331 on its inner edge, and the blade gear 331 rotates synchronously with the blade body. The blade gear 331 is a bevel gear that can rotate around the rotation axis 330 of the blade 33. The rotation axis 330 of the blade 33 is parallel to the radial direction of the blade 33. In this application, the radius of the blade 33 refers to the radius formed by connecting the center of the fan-shaped annular blade with any point on the outer arc. It can be understood that the blade rotation axis 330 is a virtual rotation axis, and the blade 33 can rotate on it. The direction of the rotation axis 330 of the blade 33 is not unique and can be designed according to needs. In some embodiments, the blade gear 331 and the blade 33 body are integrally formed. In this application, the shape of the inner or outer edge of the blade 33 matches the inner wall of the housing 11 or the outer side of the central gear, which means that when all the blades 33 are rotated to a specific position, the air valve 1 can be closed, that is, the gas is prevented from flowing through the valve body 10 of the air valve 1.

[0055] In some embodiments, the thickness of the blade 33 gradually decreases from its rotation axis 330 towards both sides. Since the rotation axis 330 is located in the middle of the blade 33, this structure improves bending stiffness by thickening the middle and reduces the load at the far end by thinning the edges, thus improving service life. It can also reduce wind resistance and noise by gradually varying the pressure gradient and avoid the generation of large-scale vortices at the edges of the blade 33.

[0056] In some embodiments, the blade 33 can be an axisymmetric structure with its rotation axis 330 as the axis of symmetry, so that the mass on both sides of the rotation axis is the same and the balance is good.

[0057] In other embodiments, the blade 33 may not adopt an axisymmetric structure, or the rotation axis 330 may be located closer to one of the sides of the blade 33.

[0058] Figure 10 It shows Figure 9 The figure shows a side view of the valve core 30. As shown, each vane gear 331 is disposed between the first two central gears 321 and the second central gear 322, and meshes with the first central gear 321 and the second central gear 322.

[0059] Multiple blades 33 include a drive blade 33A and at least two support rods concealing blades 33B.

[0060] Each support rod concealed blade 33B corresponds to a support rod 311. The support rod concealed blade 33B has a hollow sleeve 335 along its rotation axis 330. Each support rod concealed blade 33B is fitted onto the support rod 311 through its hollow sleeve 335 and can rotate around the support rod 311. With this structure, the support rod 311 can be concealed within the blade 33B.

[0061] The outer edge of the drive blade 33A is provided with a drive end 41 for connection with the drive mechanism. In some embodiments, the drive end 41 is detachably connected to the outer edge of the drive blade 33A to facilitate the replacement and reuse of the blade 33.

[0062] The drive mechanism of the damper 1 provided in this application includes: a controller configured to generate a flow control signal based on the pressure difference measured by a differential pressure sensor; and a drive motor configured to apply torque to the drive end 331 of the drive blade 33A according to the flow control signal, thereby causing the drive blade 33A to rotate by a corresponding angle. In some embodiments, the drive motor includes a drive rod and can be connected to the drive end 331 of the drive blade 33A by means of snap-fit ​​connection, magnetic attraction connection, threaded connection, etc. In some embodiments, the controller and the drive motor are disposed on the outside of the housing 11.

[0063] To facilitate understanding by those skilled in the art, the working principle of the damper 1 in this application is briefly described below. The controller of the drive mechanism calculates the rotation of the blade 33 based on parameters such as the pressure difference measured by the differential pressure sensor and the target gas flow rate through the valve body 10. It then controls the drive motor to generate torque that rotates the drive end 41 of the drive blade 33A, thereby causing the drive blade 33A to rotate around its rotation axis 330 by a corresponding angle. The blade gear 331 of the drive blade 33A drives the first central gear 321 and the second central gear 322 to rotate, thereby causing the other blades 33 to rotate around their respective rotation axes 330. When each blade 33 rotates, the angle between it and the cross-section of the housing 11 changes, thereby changing the opening of the valve core 30 and regulating the gas flow rate through the valve body 10.

[0064] This application incorporates an annular guide surface within the valve body of the air valve. This annular guide surface features multiple shark fin-shaped protrusions along its circumference, effectively reducing wind resistance. Compared to the existing annular contraction section with a constant height along its circumference, this design increases the throat cross-sectional area while simultaneously measuring a larger pressure differential, thereby reducing wind resistance. Furthermore, the valley between two adjacent protrusions can serve as a guide channel to direct gas flow, further reducing wind resistance, turbulence, vibration, and noise.

[0065] In addition, this application also improves the support structure of the valve body, completely hiding the support rod inside the blade, reducing the impact on airflow, reducing wind resistance, and also reducing the axial length of the valve body and the volume of the valve.

[0066] Those skilled in the art can understand and implement other modifications to the disclosed embodiments by reading the specification, the disclosure, the drawings, and the appended claims. In the claims, the word "comprising" does not exclude other elements and steps, and the words "a" or "an" do not exclude a plurality. In practical applications of this application, a single part may perform the function of multiple technical features referenced in the claims. Any reference numerals in the claims should not be construed as limiting the scope.

Claims

1. A damper, characterized in that, The air valve includes a valve body, a valve core, and a drive mechanism. The valve body has a cylindrical shell, and the valve core includes: A support structure includes at least two support rods and a central shaft. The central shaft is axially arranged along the centerline of the housing. Each support rod is radially arranged along the housing. One end of each support rod is fixedly connected to the central shaft, and the other end is fixedly connected to the housing. The connection points of the at least two support rods and the central shaft are located at the same height of the central shaft. A first central gear and a second central gear are sleeved on the central shaft and can rotate around the central shaft. Both the first central gear and the second central gear are bevel gears. The first central gear and the second central gear are respectively disposed on both sides of the connection point between the support rod and the central shaft. The teeth of the first central gear and the second central gear are arranged opposite to each other. The device comprises multiple fan-shaped annular blades, each with a blade gear fixedly mounted on its inner edge. The blade gear is a bevel gear rotatable about the blade's rotation axis, which is parallel to the blade's radial direction. Each blade gear is positioned between the first central gear and the second central gear and meshes with both central gears. The plurality of blades includes a drive blade and at least two support rod concealed blades. Each support rod concealed blade corresponds to a support rod. Each support rod concealed blade has a hollow sleeve along its rotation axis. Each support rod concealed blade is sleeved on the support rod through its hollow sleeve and can rotate around the support rod. The outer edge of the drive blade has a drive end connected to the drive mechanism. The drive mechanism applies torque to the drive end of the drive blade to make the drive blade rotate around its rotation axis, thereby driving the first central gear and the second central gear to rotate, thereby driving the other blades to rotate around their respective rotation axes, so as to change the opening of the valve core and thus regulate the gas flow rate through the valve body.

2. The damper of claim 1, wherein The support rod is integrally formed with the central shaft.

3. The damper as set forth in claim 1, wherein The support rod is detachably connected to the central shaft.

4. The damper of claim 3, wherein The central shaft has a connection hole at the connection point with the support rod, through which the support rod is detachably connected to the central shaft.

5. The damper as set forth in claim 1, wherein The number of support rods is three or more.

6. The damper as set forth in claim 1, wherein Each blade is an axisymmetric structure with its rotation axis as the axis of symmetry.

7. The air valve as described in claim 1, characterized in that, The drive end is detachably connected to the outer edge of the drive blade.

8. The damper as set forth in claim 1, wherein The thickness of each blade gradually decreases on both sides along its axis of rotation.

9. The air valve as described in claim 1, characterized in that: A first cavity and a second cavity that are not interconnected are provided between the inner wall and the outer wall of the housing. The inner wall of the housing is provided with a first opening that communicates with the first cavity and a second opening that communicates with the second cavity. The height of the first opening relative to the outer wall of the housing is greater than the height of the second opening relative to the outer wall of the housing. The air valve also includes a differential pressure sensor, which is in fluid communication with the first and second cavities of the valve body, and is used to measure the pressure difference between the first and second cavities.

10. The damper as set forth in claim 9, wherein The drive mechanism includes: A controller configured to generate a flow control signal based on the pressure difference measured by the differential pressure sensor; A drive motor is configured to apply torque to the drive end of the drive blade according to the flow control signal, so that the drive blade rotates by a corresponding angle.

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