Dry gas seal moving ring

Abstract

The utility model discloses a dry gas seal moving ring which comprises a ring body, a plurality of dynamic pressure grooves are formed in the face, used for making contact with a static ring, of the ring body, and all the dynamic pressure grooves are annularly and evenly distributed around the axis of the ring body. The dynamic pressure groove comprises a plurality of pressurizing grooves and a runner groove extending in the radial direction of the ring body, all the pressurizing grooves are symmetrically formed in the two sides of the runner groove and communicated with the runner groove in a branch shape, and the outer end of the runner groove penetrates through the ring body to form an air inlet. The problems that an existing bidirectional groove type moving ring is poor in dynamic pressure effect and cannot adapt to the working conditions of frequent start and stop and low-speed operation can be solved.

Description

Technical Field

[0001] This utility model relates to the field of dry gas sealing technology, specifically to a dry gas sealing dynamic ring. Background Technology

[0002] Dry gas seals are a new type of non-contact shaft seal. They are end-face seals composed of dynamic and static rings and auxiliary parts. Microscopic dynamic pressure grooves are machined on the end faces of the dynamic or static rings of the dry gas seal. During operation, due to the action of these grooves, a stable gas film with a certain rigidity is formed on the end faces of the dynamic and static rings. Under the action of this gas film, non-contact operation can be achieved between the dynamic and static rings.

[0003] The core of a dry gas seal is the dynamic pressure groove, which is divided into unidirectional grooves and bidirectional grooves. The most common unidirectional groove is the logarithmic spiral groove, which has a strong dynamic pressure effect but only supports unidirectional rotation of the seal; the herringbone groove, tree-shaped groove, and arc groove are common bidirectional grooves.

[0004] Due to its structural characteristics, the existing bidirectional groove type has a much worse dynamic pressure effect than the unidirectional groove type. This results in poor air film stiffness at the end faces of the sealing dynamic and static rings and insufficient opening force between the sealing dynamic and static rings. Especially when there are frequent starts and stops or when the seal operates at low speed, the sealing dynamic and static rings often wear.

[0005] Therefore, unless the equipment requires bidirectional rotation, unidirectional dynamic pressure grooves are currently chosen for the seals. However, with unidirectional dynamic pressure grooves, quality accidents such as reversed installation of the sealing ring during assembly at the seal factory and reversed equipment operation during on-site operations frequently occur, posing a certain safety hazard. Moreover, under certain process requirements, the equipment must rotate in both directions, in which case bidirectional dynamic pressure grooves must be used. Utility Model Content

[0006] The purpose of this invention is to provide a dry gas sealing dynamic ring that can solve the problem that the existing bidirectional groove type dynamic ring has poor dynamic pressure effect and cannot adapt to the working conditions of frequent start-stop and low-speed operation.

[0007] This utility model is achieved through the following technical solution:

[0008] A dry gas sealing dynamic ring includes a ring body. The side of the ring body that contacts a stationary ring has multiple dynamic pressure grooves. All of the dynamic pressure grooves are evenly distributed in a ring shape around the axis of the ring body. Each dynamic pressure groove includes multiple pressure-boosting grooves and flow channel grooves extending radially along the ring body. All of the pressure-boosting grooves are symmetrically arranged on both sides of the flow channel grooves and are connected to the flow channel grooves in a tree-like manner. The outer end of each flow channel groove penetrates the ring body to form an air inlet.

[0009] Optionally, the pressure-boosting groove is arc-shaped and is coaxially arranged with the ring body.

[0010] Optionally, there are two pairs of pressure-boosting grooves, namely a pair of inner pressure-boosting grooves and a pair of outer pressure-boosting grooves. The radius of the arc where the outer pressure-boosting groove is located is larger than the radius of the arc where the inner pressure-boosting groove is located. The inner pressure-boosting groove is symmetrical about the corresponding flow channel groove. The outer pressure-boosting groove is symmetrical about the corresponding flow channel groove.

[0011] Optionally, the inlet wall is beveled to make the inlet flared, and the inner end groove width of the inlet is greater than the outer end groove width; the inlet wall is smoothly connected to the groove wall of the outer booster groove.

[0012] Optionally, the ring body is coaxially provided with an annular groove, which is evenly divided into multiple pressure stabilizing grooves. The pressure stabilizing grooves correspond one-to-one with the dynamic pressure grooves. The outer wall of the pressure stabilizing groove is connected to the inner end of the corresponding flow channel groove, and the grooves are arranged symmetrically about the corresponding flow channel groove.

[0013] Optionally, the depth of both the dynamic pressure groove and the voltage stabilizing groove is 4-40 μm.

[0014] Optionally, the width of the outer end groove of the air inlet is 2-10mm, the inclination angle of the inlet wall is 30-60°, and the width of the flow channel groove is 2-10mm.

[0015] Optionally, the width of the inner pressurizing groove is 0.5-5mm, and the central angle between the two ends of each pair of inner pressurizing grooves away from the corresponding flow channel groove is 20-60°; the width of the outer pressurizing groove is 0.5-5mm, and the central angle between the two ends of each pair of outer pressurizing grooves away from the corresponding flow channel groove is 20-60°.

[0016] Optionally, the width of the voltage stabilizing groove is 0.3-3mm; when the number of dynamic pressure grooves is n and the central angle between the two ends of the voltage stabilizing groove is b, 0.3°≤(b-360° / n)*0.3≤3°.

[0017] Optionally, when the contact area between the ring body and the stationary ring is S1, and the total area of ​​the dynamic pressure groove and the stabilizing groove is S2, 0.3≤S2 / S1≤0.6.

[0018] Compared with the prior art, this utility model has the following advantages and beneficial effects:

[0019] This utility model provides a dry gas sealing dynamic ring. By setting a ring body as the base of the dynamic ring, multiple dynamic pressure grooves are formed on the side that contacts the stationary ring, allowing compressed gas to enter through these grooves and forming a gas film with a certain rigidity between the dynamic and stationary rings, thus achieving non-contact operation. Furthermore, by arranging all dynamic rings in a uniform annular distribution, the stability of the gas film is initially improved. The dynamic pressure grooves include multiple pressure-boosting grooves and radially extending flow channel grooves. The pressure-boosting grooves are symmetrically arranged in a dendritic pattern on both sides of the flow channel grooves and communicate with them, thus enhancing the flow channel grooves' stability. The outer end of the ring penetrates the ring body to form an air inlet, allowing compressed air to be forced into the flow channel groove through the air inlet, and then pressed into the dynamic pressure groove along the flow channel groove to form an air film between the moving ring and the stationary ring. Since the dynamic pressure grooves are symmetrically arranged in pairs on both sides of the flow channel groove, and the flow channel groove is arranged radially in the ring body, the dynamic pressure groove is a symmetrically arranged bidirectional groove, which can effectively avoid accidents caused by reverse installation or reverse rotation, eliminate safety hazards, and the arrangement of the flow channel groove and multiple symmetrically arranged pressure-boosting grooves can effectively improve the dynamic pressure effect of the moving ring, so that the dry gas sealing moving ring can adapt to the working conditions of frequent start-stop and low-speed operation. Attached Figure Description

[0020] The accompanying drawings, which are included to provide a further understanding of the embodiments of the present invention and form part of this application, do not constitute a limitation thereof. In the drawings:

[0021] Figure 1 A schematic diagram of the dry gas sealing ring provided in an embodiment of this utility model;

[0022] Figure 2 A partial enlarged view of the dynamic pressure groove of the dry gas sealing ring provided in an embodiment of this utility model;

[0023] Figure 3 A schematic diagram of the dimensions of the dry gas sealing ring provided in this embodiment of the utility model;

[0024] Figure 4 A schematic diagram of the compressed air flow direction when the dry gas sealing ring is stationary, provided for an embodiment of this utility model;

[0025] Figure 5 A schematic diagram of the compressed air flow direction when the dry gas sealing ring rotates, provided for an embodiment of this utility model.

[0026] The attached diagram shows the markings and corresponding component names:

[0027] 10-Annular body; 11-Air inlet; 20-Dynamic pressure groove; 21-Flow channel groove; 22-Pressure boosting groove; 221-Inner pressure boosting groove; 222-Outer pressure boosting groove; 23-Pressure stabilizing groove. Detailed Implementation

[0028] To make the objectives, technical solutions, and advantages of this utility model clearer, the present utility model will be further described in detail below with reference to the embodiments and accompanying drawings. The illustrative embodiments and descriptions of this utility model are only used to explain this utility model and are not intended to limit this utility model.

[0029] Example

[0030] Please refer to Figures 1 to 5 This embodiment provides a dry gas sealing dynamic ring, including a ring body 10. The side of the ring body 10 that contacts the stationary ring has a plurality of dynamic pressure grooves 20. All the dynamic pressure grooves 20 are evenly distributed in a ring shape around the axis of the ring body 10. The dynamic pressure grooves 20 include a plurality of pressure-boosting grooves 22 and flow channel grooves 21 extending radially along the ring body 10. All the pressure-boosting grooves 22 are symmetrically arranged on both sides of the flow channel grooves 21 and are connected to the flow channel grooves 21 in a tree-like shape. The outer end of the flow channel grooves 21 penetrates the ring body 10 to form an air inlet 11.

[0031] The dry gas sealing dynamic ring provided in this embodiment uses a ring body 10 as the base of the dynamic ring. Multiple dynamic pressure grooves 20 are formed on the side that contacts the stationary ring, allowing compressed gas to enter through the dynamic pressure grooves 20. This forms a gas film with a certain rigidity between the dynamic ring and the stationary ring, achieving non-contact operation. Furthermore, by arranging all dynamic rings in a uniform annular distribution, the stability of the gas film is initially improved. The dynamic pressure grooves 20 include multiple pressure-boosting grooves 22 and radially extending flow channel grooves 21. The pressure-boosting grooves 22 are symmetrically arranged in a dendritic pattern on both sides of the flow channel grooves 21 and communicate with them, allowing the outer ends of the flow channel grooves 21 to be continuous. The ring body 10 forms an air inlet 11, allowing compressed air to be forced into the flow channel groove 21 through the air inlet 11, and then pressed into the dynamic pressure groove 20 along the flow channel groove 21 to form an air film between the moving ring and the stationary ring. Since the dynamic pressure grooves 20 are symmetrically arranged in pairs on both sides of the flow channel groove 21, and the flow channel groove 21 is arranged radially in the ring body 10, the dynamic pressure grooves 20 are symmetrically arranged bidirectional grooves, which can effectively avoid accidents caused by reverse installation or reverse rotation, eliminate safety hazards, and the arrangement of the flow channel groove 21 and multiple symmetrically arranged pressure boosting grooves 22 can effectively improve the dynamic pressure effect of the moving ring, so that the dry gas sealing moving ring can adapt to the working conditions of frequent start-stop and low-speed operation.

[0032] To further explain the specific shape of the pressure-boosting groove 22, the pressure-boosting groove 22 is arc-shaped and is coaxially arranged with the ring body 10.

[0033] To further explain the specific arrangement of the pressure boosting grooves 22, there are two pairs of pressure boosting grooves 22, namely a pair of inner pressure boosting grooves 221 and a pair of outer pressure boosting grooves 222. The radius of the arc where the outer pressure boosting groove 222 is located is larger than the radius of the arc where the inner pressure boosting groove 221 is located. The inner pressure boosting groove 221 is arranged symmetrically with respect to the corresponding flow channel groove 21. The outer pressure boosting groove 222 is arranged symmetrically with respect to the corresponding flow channel groove 21.

[0034] To facilitate the compression of compressed air from the inlet 11 into the flow channel groove 21, the inlet wall of the inlet 11 is inclined, so that the inlet 11 is in the shape of a trumpet, and the inner end groove width of the inlet 11 is greater than the outer end groove width; the inlet wall of the inlet 11 is smoothly connected to the groove wall of the outer pressure groove 222.

[0035] With the above configuration, when the ring body 10 rotates, the inclined inlet wall allows the compressed gas to flow in more smoothly and diffuse into the flow channel groove 21. Furthermore, the compressed gas entering the flow channel groove 21 can flow into the outer pressure groove 222 more smoothly, thereby increasing the pressure of the gas entering the outer pressure groove 222 and further increasing the opening force between the moving ring and the stationary ring.

[0036] To further increase the opening force between the dynamic ring and the stationary ring, the ring body 10 is coaxially provided with an annular groove. The annular groove is evenly divided into multiple pressure stabilizing grooves 23. The pressure stabilizing grooves 23 correspond one-to-one with the dynamic pressure grooves 20. The outer wall of the pressure stabilizing groove 23 is connected to the inner end of the corresponding flow channel groove 21 and is arranged symmetrically with respect to the corresponding flow channel groove 21.

[0037] With the above configuration, when the ring 10 rotates, the compressed air is forced into the booster groove 21 through the flow channel groove 21, which further increases the air pressure and increases the opening force between the moving ring and the stationary ring. At the same time, some of the compressed air flows into and fills the pressure stabilizing groove 23, and then circulates continuously within it to form a ring-shaped air film between the moving ring and the stationary ring. This will further increase the opening force between the moving ring and the stationary ring and ensure that every point on the circumference of the ring is uniformly stressed, thereby further improving the stability of the air film.

[0038] Please Figure 1 and Figure 2 Based on reference Figure 3 Preferably, in this embodiment, the depth of both the dynamic pressure groove 20 and the pressure stabilizing groove 23 is 4-40μm.

[0039] Preferably, in this embodiment, the outer end groove width (L1) of the air inlet 11 is 2-10mm, the inclination angle (angle c) of the inlet wall of the air inlet 11 is 30-60°, and the groove width (L2) of the flow channel groove 21 is 2-10mm.

[0040] Preferably, in this embodiment, the width of the inner pressure boosting groove 221 is 0.5-5mm, and the central angle (angle a) between the two ends of each pair of inner pressure boosting grooves 221 away from the corresponding flow channel groove 21 is 20-60°; the width of the outer pressure boosting groove 222 is 0.5-5mm, and the central angle (angle a) between the two ends of each pair of outer pressure boosting grooves 222 away from the corresponding flow channel groove 21 is 20-60°.

[0041] Preferably, in this embodiment, the width of the voltage stabilizing groove 23 is 0.3-3mm; when the number of dynamic pressure grooves 20 is n and the central angle between the two ends of the voltage stabilizing groove 23 is b, 0.3°≤(b-360° / n)*0.3≤3°.

[0042] Preferably, in this embodiment, when the contact area between the ring body 10 and the stationary ring is S1, and the total area of ​​the dynamic pressure groove 20 and the stabilizing groove 23 is S2, 0.3≤S2 / S1≤0.6.

[0043] The specific embodiments described above further illustrate the purpose, technical solution, and beneficial effects of this utility model. It should be understood that the above description is only a specific embodiment of this utility model and is not intended to limit the scope of protection of this utility model. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the scope of protection of this utility model.

Claims

1. A dry gas sealing dynamic ring, characterized in that, Includes a ring body (10), wherein the side of the ring body (10) that is in contact with the stationary ring is provided with a plurality of dynamic pressure grooves (20), and all of the dynamic pressure grooves (20) are uniformly distributed in a ring shape around the axis of the ring body (10); The dynamic pressure groove (20) includes multiple pressure boosting grooves (22) and a flow channel groove (21) extending radially along the ring body (10). All the pressure boosting grooves (22) are symmetrically arranged on both sides of the flow channel groove (21) and are connected to the flow channel groove (21) in a tree-like manner. The outer end of the flow channel groove (21) penetrates the ring body (10) to form an air inlet (11).

2. The dry gas sealing dynamic ring according to claim 1, characterized in that, The pressure-boosting groove (22) is arc-shaped and is coaxially arranged with the ring (10).

3. The dry gas sealing dynamic ring according to claim 2, characterized in that, The number of the booster grooves (22) is two pairs, namely a pair of inner booster grooves (221) and a pair of outer booster grooves (222). The radius of the arc where the outer booster groove (222) is located is greater than the radius of the arc where the inner booster groove (221) is located. The internal pressure boosting groove (221) is arranged symmetrically about the corresponding flow channel groove (21); The external pressure boosting groove (222) is arranged symmetrically about the corresponding flow channel groove (21).

4. The dry gas sealing dynamic ring according to claim 3, characterized in that, The inlet wall of the air inlet (11) is inclined so that the air inlet (11) is in the shape of a trumpet, and the inner end groove width of the air inlet (11) is greater than the outer end groove width. The inlet wall of the air inlet (11) is smoothly connected to the groove wall of the external pressure boosting groove (222).

5. The dry gas sealing dynamic ring according to claim 4, characterized in that, The ring body (10) is coaxially provided with an annular groove, which is evenly divided into multiple pressure stabilizing grooves (23). The pressure stabilizing grooves (23) correspond one-to-one with the dynamic pressure grooves (20). The outer wall of the pressure stabilizing groove (23) is connected to the inner end of the corresponding flow channel groove (21), and is symmetrically arranged with the corresponding flow channel groove (21) as the axis.

6. The dry gas sealing dynamic ring according to claim 5, characterized in that, The depth of both the dynamic pressure groove (20) and the stabilizing groove (23) is 4-40 μm.

7. The dry gas sealing dynamic ring according to claim 6, characterized in that, The outer end groove width of the air inlet (11) is 2-10mm, the inclination angle of the inlet wall of the air inlet (11) is 30-60°, and the groove width of the flow channel groove (21) is 2-10mm.

8. The dry gas sealing dynamic ring according to claim 7, characterized in that, The width of the internal pressure boosting groove (221) is 0.5-5mm, and the central angle between the two ends of each pair of internal pressure boosting grooves (221) away from the corresponding flow channel groove (21) is 20-60°. The width of the external pressure boosting groove (222) is 0.5-5mm, and the central angle between the two ends of each pair of external pressure boosting grooves (222) away from the corresponding flow channel groove (21) is 20-60°.

9. The dry gas sealing dynamic ring according to claim 8, characterized in that, The width of the voltage stabilizing groove (23) is 0.3-3mm; When the number of dynamic pressure grooves (20) is n and the central angle between the two ends of the stabilizing groove (23) is b, 0.3°≤(b-360° / n)*0.3≤3°.

10. The dry gas sealing dynamic ring according to claim 9, characterized in that, When the contact area between the ring body (10) and the stationary ring is S1, and the total area of ​​the dynamic pressure groove (20) and the stabilizing groove (23) is S2, 0.3≤S2 / S1≤0.6.

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