A cylindrical air film sealing structure with toothed pressure groove

Abstract

This application relates to a cylindrical gas film sealing structure with toothed pressure-boosting grooves. The cylindrical gas film sealing structure with toothed pressure-boosting grooves includes: a rear end cap and a front end cap fitted onto a floating ring and a rotating ring; and several toothed pressure-boosting grooves arranged in an evenly spaced circular array on the outer circumferential surface of the rotating ring. Each toothed pressure-boosting groove includes a toothless feature groove area a and a toothed feature groove area b. Compared to the traditional straight groove design, this application creates several toothed pressure-boosting grooves in an evenly spaced circular array on the outer circumferential surface of the rotating ring. The toothed feature groove area b of the toothed pressure-boosting groove has a toothed structure protruding into the groove. The toothed structure forms a contracting channel along the gas flow direction, so that when gas flows from the toothless feature groove area a into the toothed feature groove area b, the cross-sectional area of ​​the flow channel decreases along the gas flow direction, thereby enhancing the hydrodynamic pressure effect, increasing the gas film buoyancy, improving the support for the floating ring, enhancing the gas film stability, and thus reducing leakage and improving sealing performance.

Description

Technical Field

[0001] This application relates to the field of cylindrical air film sealing technology, and in particular to a cylindrical air film sealing structure with a toothed pressure-boosting groove. Background Technology

[0002] With the increasing demand for sealing technology in fields such as aerospace and petrochemicals, the importance of sealing technology in production and science and technology is receiving more and more attention from researchers.

[0003] Cylindrical film sealing is a novel non-contact sealing technology based on micron-level film lubrication, offering advantages such as low leakage and suitability for high-speed and high-pressure applications. Its working principle is based on hydrodynamic lubrication theory, and the specific process is as follows: During operation, the rotating ring and floating ring are eccentrically mounted. As the rotor rotates, the gas within the sealing gap is driven from the side with the larger gap to the side with the smaller gap by boundary friction. As the film gap gradually converges, the gas is compressed, resulting in increased pressure—this phenomenon is known as hydrodynamic effect. Under this hydrodynamic pressure, the floating ring moves towards the center of the rotating ring, gradually reducing the eccentricity between them until they become concentric, entering a stable operating state. When the sealing system is disturbed and becomes eccentric, causing the gap on one side to decrease, the hydrodynamic effect causes the floating ring to shift to the side with the thicker film, restoring a new equilibrium. Through this dynamic adjustment process, the hydrodynamic pressure, the force generated by the deformation of the floating ring, and the gas friction force achieve mutual balance, ensuring the stability and effectiveness of the sealing system.

[0004] Traditional cylindrical gas film seal structures typically employ a single-slot design, where a straight groove is created on the surface of the rotating ring. However, due to its uniform shape, it is difficult to effectively constrain the flow direction and velocity of the gas. As the rotating ring rotates at high speed, the gas tends to form a turbulent flow state within the groove, failing to flow along the expected path. Consequently, the gas cannot fully utilize its dynamic pressure effect, limiting its support for the floating ring and thus reducing sealing performance. Summary of the Invention

[0005] To solve or partially solve the problems existing in the related technologies, this application provides a cylindrical air film sealing structure with a toothed pressure-boosting groove.

[0006] To achieve the above objectives, this application employs the following technical solution:

[0007] A cylindrical gas film sealing structure for a toothed booster groove includes a floating ring, a moving ring, and a main shaft. A micron-level cylindrical gas film is formed between the floating ring and the moving ring. The cylindrical gas film sealing structure for the toothed booster groove further includes:

[0008] The rear end cap and front end cap are fitted onto the float ring and the moving ring;

[0009] A number of toothed pressure-boosting grooves are arranged in an equally spaced circular array on the outer circumferential surface of the moving ring. Each toothed pressure-boosting groove includes a toothless feature groove area a and a toothed feature groove area b.

[0010] The toothed feature groove region b is provided with a tooth-like structure protruding into the groove. The tooth-like structure forms a contracting channel along the gas flow direction, so that when the gas flows into the toothed feature groove region b from the toothless feature groove region a, the cross-sectional area of ​​the flow channel decreases along the gas flow direction.

[0011] Optionally, a plurality of flexible goose-shaped support members are provided between the floating ring and the rear end cover.

[0012] Optionally, the wingtip portion of the flexible goose-shaped support has an arc shape that matches the outer periphery of the floating ring, and the radius of the arc shape is consistent with the radius of the outer periphery of the floating ring.

[0013] Optionally, the float ring is connected to the front end cover via a locating pin, and the float ring is connected to the rear end cover via a spring.

[0014] Optionally, the rear end cover and the front end cover are connected by hexagon socket bolts, and a sealing ring is provided at the connection between the two.

[0015] Optionally, the side of the cylindrical gas film closer to the rear end cover is the high-pressure gas side, and the side closer to the front end cover is the low-pressure gas side.

[0016] Optionally, the cylindrical region between adjacent toothed pressurizing grooves and the cylindrical region between the toothed pressurizing grooves and the low-pressure gas side form a sealing dam.

[0017] Optionally, the groove end of the toothed booster groove extends outward along its axial direction to communicate with the high-pressure gas side, thereby forming an air inlet.

[0018] Optionally, the bottom end of the toothed pressure-boosting groove extends axially inward to the sealing dam to form the groove root.

[0019] Optionally, the toothless feature groove area a forms the leeward side, and the toothed feature groove area b forms the windward side.

[0020] The beneficial effects of this application are as follows: Compared with the traditional straight groove design, this application opens several toothed pressure-boosting grooves in a circular array at equal intervals on the outer circumferential surface of the moving ring. The toothed feature groove area b of the toothed pressure-boosting groove has a toothed structure that protrudes into the groove. The toothed structure forms a contracting channel along the gas flow direction, so that when the gas flows into the toothed feature groove area b from the toothless feature groove area a, the cross-sectional area of ​​the flow channel decreases along the gas flow direction, thereby enhancing the hydrodynamic pressure effect, increasing the gas film buoyancy, improving the support for the floating ring, enhancing the stability of the gas film, and thus reducing leakage and improving the sealing performance.

[0021] It should be understood that the above general description and the following detailed description are exemplary and explanatory only, and do not limit this application. Attached Figure Description

[0022] The above and other objects, features and advantages of this application will become more apparent from the more detailed description of exemplary embodiments thereof in conjunction with the accompanying drawings, wherein the same reference numerals generally represent the same components in the exemplary embodiments thereof.

[0023] Figure 1 This is a schematic diagram of the cylindrical air film sealing structure shown in the embodiments of this application;

[0024] Figure 2 This is a schematic diagram of the toothed pressure-boosting groove shown in the embodiments of this application;

[0025] Figure 3 This is a three-dimensional structural schematic diagram of the flexible goose-shaped support member shown in the embodiments of this application;

[0026] Figure 4 This is a side view of the flexible goose-shaped support shown in an embodiment of this application;

[0027] Figure 5 This is a cross-sectional schematic diagram of the cylindrical air film sealing structure shown in the embodiments of this application;

[0028] Figure 6 This is a detailed diagram showing the installation of the sealing ring according to an embodiment of this application.

[0029] Reference numerals: 1. Rear end cover, 2. Hex socket head cap bolt, 3. Sealing ring, 4. Flexible goose-shaped support, 5. Spring, 6. Floating ring, 7. Moving ring, 8. Main shaft, 9. Positioning pin, 10. Front end cover, 11. Toothed pressure groove, 12. Wing tip section, 13. Goose wing section. Detailed Implementation

[0030] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0031] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this application, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0032] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between components; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application as appropriate to the specific circumstances.

[0033] In this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0034] In this application, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0035] Although the embodiments of the present application have been shown and described above, it can be understood that the above embodiments are exemplary and cannot be understood as limitations on the present application. Ordinary technicians in this field can change, modify, replace and modify the above embodiments within the scope of the present application.

[0036] The above description is merely an optional embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

[0037] To make the objectives, technical solutions, and beneficial effects of this application clearer, the preferred embodiments of this application will be described in detail below with reference to the accompanying drawings, so as to facilitate understanding by those skilled in the art.

[0038] Example 1:

[0039] See Figure 1 and Figure 2 A cylindrical gas film sealing structure for a toothed booster groove includes a floating ring 6, a moving ring 7, and a main shaft 8. A micron-level cylindrical gas film is formed between the floating ring 6 and the moving ring 7. The cylindrical gas film sealing structure for the toothed booster groove further includes:

[0040] The rear end cap 1 and the front end cap 10 are fitted onto the floating ring 6 and the moving ring 7;

[0041] A plurality of toothed pressure-boosting grooves 11 are arranged in an equally spaced circular array on the outer peripheral surface of the moving ring 7. Each toothed pressure-boosting groove 11 includes a toothless feature groove area a and a toothed feature groove area b.

[0042] The toothed feature groove region b is provided with a tooth-like structure protruding into the groove. The tooth-like structure forms a contracting channel along the gas flow direction, so that when the gas flows into the toothed feature groove region b from the toothless feature groove region a, the cross-sectional area of ​​the flow channel decreases along the gas flow direction.

[0043] Specifically, the moving ring 7 is coaxially mounted on the main shaft 8, and the main shaft 8 and the moving ring 7 are interference-fitted to ensure that the main shaft 8 rotates the moving ring 7 at high speed. The floating ring 6 is eccentrically mounted on the moving ring 7. One end of the floating ring 6 is mounted on the front end cover 10, and the other end is mounted on the rear end cover 1. The front end cover 10 is connected to the rear end cover 1, and the rear end cover 1 is mounted on an external device.

[0044] The outer circumferential surface of the moving ring 7 is provided with a plurality of toothed pressure-boosting grooves 11 arranged in an equally spaced circular array. Each toothed pressure-boosting groove 11 includes a toothless characteristic groove region a and a toothed characteristic groove region b. From a macroscopic perspective, when gas flows within the toothed pressure-boosting grooves 11, the presence of the teeth is equivalent to adding many protrusions and depressions to the originally relatively smooth flow channel. When gas flows from the region of the toothless characteristic groove region a to the region of the toothed characteristic groove region b, the gas needs to flow between these teeth. The space between the teeth is relatively narrow, forming a contracting channel, which reduces the effective cross-sectional area through which the gas flows.

[0045] In the toothed pressure booster trough 11, the gas flow direction is not entirely linear, but is altered by the toothed structure. When gas flows into the toothed region, it is forced to flow along the contour and angle of the tooth, and this change in flow direction causes gas to converge in local areas. During the convergence process, the originally dispersed gas flows in a smaller space, resulting in a reduction in cross-sectional area.

[0046] Compared to the traditional straight groove, the unique toothed structure of the toothed feature groove region b allows for a more regular flow direction of gas after it enters the groove due to the obstruction and guidance of the groove wall. When the moving ring 7 rotates at high speed, the gas flows along the specific path of the toothed pressurizing groove 11, making it less prone to turbulence. When the gas flows from the non-toothed feature groove region a into the toothed feature groove region b, the flow velocity and direction can be effectively controlled under the effect of the change in cross-sectional area, allowing for better flow from the high-pressure side to the low-pressure side, forming a stable gas film, and enhancing the guiding effect on the gas.

[0047] Under complex operating conditions, the toothed pressure-boosting groove 11 can optimize gas flow and pressure distribution. On the one hand, when gas flows through the toothed pressure-boosting groove 11, the cross-sectional area of ​​the gas channel changes due to the toothed structure. According to the law of conservation of flow rate, the gas velocity will change, resulting in dynamic pressure changes. The toothed feature of the toothed groove region b increases the gas velocity and dynamic pressure, forming a more reasonable pressure gradient within the sealing gap. On the other hand, when the floating ring 6 shifts due to external interference, the toothed pressure-boosting groove 11 can adjust the gas flow and pressure distribution according to the position change of the floating ring 6. For example, when the gap on one side becomes smaller, the toothed pressure-boosting groove 11 can guide more gas to that side, increasing the gas pressure on that side, causing the floating ring 6 to shift to the side with a thicker gas film, restoring the equilibrium state, and improving the adaptability of the gas film seal under complex operating conditions.

[0048] When the main shaft 8 rotates at a predetermined speed, the gas flows along the shaft due to viscous friction, flowing from the side with a larger gap between the moving ring 7 and the floating ring 6 (in eccentric installation) to the side with a smaller gap. Under the action of the converging gap, the gas is compressed, resulting in increased pressure and forming a gas film several micrometers thick in this area. Simultaneously, the toothed pressure-boosting groove 11 on the moving ring 7 significantly enhances the dynamic pressure effect. Multiple changes in cross-sectional area continuously increase the dynamic pressure, providing stronger buoyancy to the floating ring 6. Under complex operating conditions such as high speed and high pressure difference, this enhanced dynamic pressure effect effectively improves the load-bearing capacity of the gas film, ensuring a stable non-contact state between the floating ring 6 and the moving ring 7, reducing leakage, and meeting the high-performance requirements of aero-engines for gas film sealing. As the fluid dynamic pressure on the floating ring 6 exceeds the sum of its own weight and friction, the floating ring 6 moves towards the geometric center, resulting in a decrease in eccentricity and thus reducing the fluid dynamic pressure. When the fluid dynamic pressure is lower than the sum of the weight and friction of the floating ring 6, the floating ring 6 moves in the opposite direction. Through this repeated motion, the fluid dynamic pressure, gravity, and friction eventually reach a dynamic equilibrium, completing the fluid sealing process.

[0049] In summary, compared to the traditional single-groove design, this application creates several toothed pressure-boosting grooves 11 in a circumferential array at equal intervals on the outer surface of the moving ring 7. The toothed feature groove area b of the toothed pressure-boosting groove 11 has a toothed structure protruding into the groove. The toothed structure forms a contracting channel along the gas flow direction, so that when the gas flows into the toothed feature groove area b from the toothless feature groove area a, the cross-sectional area of ​​the flow channel decreases along the gas flow direction, thereby enhancing the hydrodynamic pressure effect, increasing the gas film buoyancy, improving the support for the floating ring, enhancing the stability of the gas film, and thus reducing leakage and improving sealing performance.

[0050] Example 2:

[0051] See Figure 3 and Figure 4 Based on Embodiment 1, optionally, a plurality of flexible goose-shaped support members 4 are provided between the floating ring 6 and the rear end cover 1.

[0052] Optionally, the wingtip portion 12 of the flexible goose-shaped support 4 has an arc shape that matches the outer periphery of the floating ring 6, and the radius of the arc shape is consistent with the radius of the outer periphery of the floating ring 6.

[0053] Specifically, one end of the flexible goose-shaped support 4 is fixed to the inner wall of the rear end cover 1, and the other end contacts the outer wall of the floating ring 6. Due to the continuous change in the position of the floating ring 6, the goose wing portion 13 of the flexible goose-shaped support 4 will undergo elastic deformation, continuously supporting the floating ring 6. After the operation stops, the arc-shaped structure of the wingtip portion 12 will help the floating ring return to the correct eccentric position, playing a positioning role.

[0054] In this embodiment, by setting the flexible goose-shaped support 4, collision and friction between the sealing pairs can be avoided under large radial displacement, preventing seal failure. This ensures that the floating ring maintains correct eccentric installation even after frequent start-stop of the sealing mechanism and under external force, guaranteeing the reliability of the sealing structure. In addition, the flexible goose-shaped support 4 has the characteristic of adjusting stiffness and damping through deformation, enabling stable operation under complex working conditions.

[0055] Example 3:

[0056] See Figure 5 and Figure 6 Based on the above embodiments, optionally, the floating ring 6 is connected to the front end cover 10 by a positioning pin 9, and the floating ring 6 is connected to the rear end cover 1 by a spring 5.

[0057] Specifically, the positioning pin 9 is used to ensure the accurate relative position of the floating ring 6 and the front cover 10 during assembly, avoiding sealing failure or mechanical interference due to positional deviation. During equipment operation, the positioning pin can prevent the floating ring 6 from rotating or moving axially relative to the front cover 10. The positioning pin 9 provides guidance for disassembly and assembly, shortens maintenance time, and avoids damage to parts due to human alignment errors. The positioning pin 9 can also act as a "guide post" to help quickly align the installation position of the floating ring 6 and the front cover 10, improving installation efficiency.

[0058] One end of the spring 5 is connected to the float ring 6, and the other end is connected to the rear end cover 1. The elastic deformation capacity of the spring 5 can absorb the axial / radial displacement of the float ring 6 and the rear end cover 1 caused by temperature changes or processing errors, and avoid stress concentration caused by rigid connection. The flexibility of the spring 5 can attenuate the vibration or impact during equipment operation and protect the float ring 6 and the rear end cover 1 from fatigue damage.

[0059] Optionally, the rear end cover 1 and the front end cover 10 are connected by hexagon socket bolts 2, and a sealing ring 3 is provided at the connection between the two.

[0060] Specifically, the rear cover 1 and the front cover 10 are tightly connected by hex bolts 2, and the use of hex bolts 2 facilitates disassembly in confined spaces;

[0061] In this embodiment, the sealing ring 3 is installed in the groove between the rear end cover 1 and the front end cover 10. As a static seal, the sealing ring 3 fills the microscopic gaps at the end cover mating surfaces, preventing external gas / liquid from directly intruding into the sealing structure and avoiding interference from external pressure fluctuations with the pressure field of the toothed groove gas film. The toothed pressure-boosting groove 11 achieves non-contact sealing by relying on the gas film thickness (typically at the micrometer level). The sealing ring 3 prevents environmental media penetration that could lead to gas film dilution or local pressure imbalance, ensuring uniform gas film load-bearing. In this way, the sealing ring 3 ensures that the internal pressure distribution of the cylindrical gas film sealing structure of the toothed pressure-boosting groove 11 is unaffected by external factors.

[0062] Optionally, the side of the cylindrical gas film closer to the rear end cover 1 is the high-pressure gas side, and the side closer to the front end cover 10 is the low-pressure gas side.

[0063] Specifically, a gas film pressure gradient is formed between the high-pressure gas side and the low-pressure gas side to drive the gas film flow. The gas film pressure gradient counteracts the radial force of the shaft system, ensuring that the floating ring 6 and the moving ring 7 do not directly contact each other, thereby reducing frictional power consumption. When the operating conditions fluctuate (such as pressure and temperature changes) and the gas film thickness decreases, the high-pressure side gas automatically compensates through the throttling effect of the tooth groove to maintain the gas film stiffness. During startup / shutdown, the pressure gradient helps to quickly establish the gas film and avoid dry friction.

[0064] Optionally, the cylindrical region between the adjacent toothed pressurizing grooves 11 and the cylindrical region between the toothed pressurizing grooves 11 and the low-pressure gas side form a sealing dam.

[0065] Specifically, the toothed pressure-boosting groove 11 is a concave structure, and the sealing dam is a raised area between adjacent toothed pressure-boosting grooves 11. The two work together to form a unique alternating "tooth-groove-dam" structure. The sealing dam decomposes the pressure difference (ΔP) from the high-pressure side to the low-pressure side into multiple stages. The sealing dam between adjacent toothed grooves reduces the flow area, forcing the gas to generate a local throttling effect when passing through the narrow gap, forming a stepped pressure drop. Multi-stage throttling can significantly reduce the leakage rate. The raised structure of the sealing dam induces local vortices in the gas when rotating, forming a high-pressure air cushion layer. This pressure distribution can counteract the radial force of the shaft system, keeping the floating ring 6 and the moving ring 7 in a stable gas film gap.

[0066] Optionally, the groove end of the toothed booster groove 11 extends outward along its axial direction to communicate with the high-pressure gas side, thereby forming an air inlet.

[0067] Specifically, the gas is introduced into the toothed booster groove 11 through the air inlet, and the high-pressure gas is precisely introduced into the toothed booster groove 11 through the air inlet to avoid turbulence.

[0068] Optionally, the bottom end of the toothed pressure-boosting groove 11 extends along its axial inner side to the sealing dam to form the groove root.

[0069] Specifically, the groove root extends to form a gradually changing channel, guiding the gas to diffuse smoothly, promoting uniform gas film distribution, and improving gas film stiffness. By controlling the gas flow path, the gas film thickness becomes more stable, enhancing the isolation effect of the sealing surface and reducing friction and wear. The groove root and the sealing dam work together to form a multi-stage throttling structure. When gas flows through the groove root, the throttling effect is generated through the contraction and expansion of the channel, reducing gas pressure, effectively blocking leakage paths, and reducing the amount of media leakage. The groove root connects the toothed pressure-boosting groove 11 and the sealing dam, optimizing the structural stress distribution, reducing stress concentration, improving the deformation resistance of the sealing assembly, and extending its service life, especially ensuring the stability of the sealing system under high pressure and high speed conditions.

[0070] Optionally, the toothless feature groove area a forms the leeward side, and the toothed feature groove area b forms the windward side.

[0071] Specifically, the width of each toothed pressurizing groove 11 forms a windward side and a leeward side on both sides. The windward side is the side of the toothed pressurizing groove 11 with toothed features, and the windward side faces the inlet gas entering the toothed pressurizing groove 11. The leeward side is the side without toothed features. When the gas flows from the toothless groove area a into the toothed groove area b at a certain speed, the flow velocity increases and the dynamic pressure increases in order to maintain the flow rate in order to keep the flow rate constant as the cross-sectional area of ​​the gas decreases.

[0072] It should be noted that the structures and / or installation methods not detailed in this application are those that can be known by those skilled in the art in combination with common knowledge and / or prior art, and are not the focus of this application, and will not be elaborated further here.

[0073] Finally, it should be noted that the above preferred embodiments are only used to illustrate the technical solutions of this application and are not intended to limit it. Although this application has been described in detail through the above preferred embodiments, those skilled in the art should understand that various changes can be made to it in form and detail without departing from the scope defined by the claims of this application; the dimensions of the drawings are not related to the specific physical object, and the physical object dimensions can be arbitrarily changed.

Claims

1. A cylindrical gas film sealing structure for a toothed pressure-boosting groove, comprising a floating ring (6), a moving ring (7), and a main shaft (8), wherein a micron-level cylindrical gas film is formed between the floating ring (6) and the moving ring (7), characterized in that, The cylindrical air film sealing structure of the toothed pressurization groove further includes: The rear end cap (1) and the front end cap (10) are fitted onto the floating ring (6) and the moving ring (7); A number of toothed pressure-boosting grooves (11) are arranged in an equally spaced circular array on the outer circumferential surface of the moving ring (7). Each toothed pressure-boosting groove (11) includes a toothless feature groove area a and a toothed feature groove area b. The toothed feature groove region b is provided with a tooth-like structure protruding into the groove. The tooth-like structure forms a contracting channel along the gas flow direction, so that when the gas flows into the toothed feature groove region b from the toothless feature groove region a, the cross-sectional area of ​​the flow channel decreases along the gas flow direction.

2. The cylindrical air film sealing structure of the toothed pressurizing groove as described in claim 1, characterized in that, Several flexible goose-shaped support members (4) are provided between the floating ring (6) and the rear end cover (1).

3. The cylindrical air film sealing structure of the toothed pressurizing groove as described in claim 2, characterized in that, The wingtip portion (12) of the flexible goose-shaped support (4) has an arc shape that matches the outer periphery of the float ring (6), and the radius of the arc shape is consistent with the outer periphery radius of the float ring (6).

4. The cylindrical air film sealing structure of the toothed pressurization groove as described in claim 1 or 2, characterized in that, The floating ring (6) is connected to the front cover (10) by a positioning pin (9), and the floating ring (6) is connected to the rear cover (1) by a spring (5).

5. The cylindrical air film sealing structure of the toothed pressurizing groove as described in claim 4, characterized in that, The rear end cover (1) and the front end cover (10) are connected by hexagonal socket head caps (2), and a sealing ring (3) is provided at the connection between the two.

6. The cylindrical air film sealing structure of the toothed pressurizing groove as described in claim 1, characterized in that, The cylindrical gas film has a high-pressure gas side on the side near the rear end cover (1) and a low-pressure gas side on the side near the front end cover (10).

7. The cylindrical air film sealing structure of the toothed pressurizing groove as described in claim 6, characterized in that, The cylindrical area between adjacent toothed booster grooves (11) and the cylindrical area between the toothed booster grooves (11) and the low-pressure gas side form a sealing dam.

8. The cylindrical air film sealing structure of the toothed pressurizing groove as described in claim 7, characterized in that, The slot end of the toothed booster groove (11) extends outward along its axial direction to communicate with the high-pressure gas side to form an air inlet.

9. The cylindrical air film sealing structure of the toothed pressurizing groove as described in claim 8, characterized in that, The bottom end of the toothed pressure-boosting groove (11) extends along its axial inner side to the sealing dam to form the groove root.

10. The cylindrical air film sealing structure of the toothed pressurizing groove as described in claim 1, characterized in that, The toothless feature groove area a forms the leeward side, and the toothed feature groove area b forms the windward side.

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