Rotary machine dynamic-static gap sealing structure, rotary machine device, and air circulating machine

Abstract

The utility model provides a kind of rotary machine dynamic static gap sealing structure, rotary machine device and air circulating machine, rotary machine dynamic static gap sealing structure includes sealing ring and transmission shaft, transmission shaft can rotate through the inner ring hole of sealing ring around its own axis, there is dynamic static gap between the hole peripheral wall surface of inner ring hole and the outer peripheral wall surface of transmission shaft, dynamic static gap is between 0.25 millimeter to 0.45 millimeter, multiple square cavities are arranged in the concave of hole peripheral wall surface, multiple square cavities are arranged in the circumferential direction and axial direction of inner ring hole, the length of side of each square cavity is between 0.5 millimeter to 3.0 millimeter, and each square cavity satisfies that the proportion coefficient is between 0.17 to 0.21, stable non-contact sealing is formed between sealing ring and transmission shaft, to avoid the phenomenon of friction, wear, eliminate abnormal noise, improve the operating efficiency and stability of transmission shaft, and strong damping effect is obtained at dynamic static gap, to enhance sealing effect, and then effectively reduce gas leakage.

Description

Technical Field

[0001] This utility model relates to the field of rotating machinery dynamic and static clearance sealing technology, and in particular to a rotating machinery dynamic and static clearance sealing structure, a rotating machinery device having the rotating machinery dynamic and static clearance sealing structure, and an air circulator. Background Technology

[0002] The air circulator is a core component of an aircraft's environmental control system. It uses a compressor and turbine to achieve compression and expansion processes respectively, while a fan drives the air to remove heat from the heat exchanger. The compressor, turbine, fan, and drive shaft in the air circulator form a rotor assembly, which is supported by an air bearing system for high-speed rotation. Because the fan is located close to ambient pressure, while the internal pressure of the air circulator is close to 3-4 bara, the pressure difference causes high-pressure gas to flow to the fan location and be expelled to the outside. This can lead to gas leakage from the air circulator. Excessive leakage will affect the operating efficiency and stability of the air circulator.

[0003] To reduce gas leakage, the current method involves installing a seal around the drive shaft of the air circulator. Since the rotor assembly of the air circulator is a high-speed moving part with a rotation speed of approximately 60,000 rpm, the seal and the drive shaft are sealed using a non-contact method. As a result, the inner wall of the existing seal has an annular groove, and the outer wall of the drive shaft has an annular protrusion. The annular protrusion on the outer wall of the drive shaft is inserted into the annular groove on the inner wall of the annular seal, creating a close fit between the annular protrusion and the annular groove. This creates a strong flow obstruction to the airflow along the outer surface of the drive shaft.

[0004] However, in actual operation, the drive shaft inevitably experiences axial fretting. Furthermore, under prolonged high-pressure gas impact, the annular protrusion of the drive shaft and the annular groove of the seal inevitably deform in the circumferential direction of the drive shaft. Because the annular protrusion designed on the outer circumferential wall of the existing drive shaft is inserted into the annular groove constructed on the inner circumferential wall of the annular seal, there will be contact friction between the annular protrusion of the drive shaft and the annular groove of the seal, generating abnormal noise and affecting the rotational efficiency and stability of the drive shaft. Once wear failure occurs between the annular protrusion of the drive shaft and the annular groove of the seal, a large amount of gas will leak out, resulting in poor sealing performance. Utility Model Content

[0005] To achieve the primary objective of this invention, it provides a sealing structure for the dynamic and static gaps of rotating machinery. By forming a stable non-contact seal between the sealing ring and the transmission shaft, friction and wear are avoided, thereby eliminating abnormal noise, improving the rotational efficiency and stability of the transmission shaft, and obtaining a strong damping effect at the dynamic and static gaps formed between the sealing ring and the transmission shaft to enhance the sealing effect and effectively reduce gas leakage.

[0006] To achieve the second objective of this utility model, this utility model provides a rotating mechanical device having the above-mentioned rotating mechanical dynamic-static gap sealing structure.

[0007] To achieve the third objective of this utility model, this utility model provides an air circulator having the above-mentioned rotating machinery dynamic and static gap sealing structure.

[0008] To achieve the primary objective of this invention, a sealing structure for the dynamic-static clearance of rotating machinery is provided, comprising a sealing ring and a drive shaft. The drive shaft rotatably passes through the inner annular hole of the sealing ring around its own axis. The sealing ring is stationary, and a dynamic-static clearance exists between the peripheral wall of the inner annular hole and the outer peripheral wall of the drive shaft. Between movement and stillness Between 0.25 mm and 0.45 mm, multiple square cavities are recessed into the periphery of the hole. These square cavities are arranged circumferentially and axially in the inner annular hole, and the side length of each square cavity is... The diameter is between 0.5 mm and 3.0 mm, and each square cavity satisfies the scaling factor. Between 0.17 and 0.21, The cavity depth of the square cavity in the radial direction of the inner annular hole.

[0009] A further option is that multiple square cavities are arranged at equal intervals in the circumferential direction of the inner annular hole; and / or, multiple square cavities are arranged at equal intervals in the axial direction of the inner annular hole.

[0010] A further embodiment is that the circumferential spacing between two adjacent square cavities in the inner annular hole is between 0.1 mm and 0.3 mm; and / or, the axial spacing between two adjacent square cavities in the inner annular hole is between 0.1 mm and 0.3 mm.

[0011] A further approach is to ensure that each square cavity satisfies a scaling factor. It is 0.19.

[0012] To achieve the second objective of this utility model, this utility model provides a rotating mechanical device, including a rotating mechanical dynamic-static gap sealing structure, wherein the rotating mechanical dynamic-static gap sealing structure is the aforementioned rotating mechanical dynamic-static gap sealing structure.

[0013] To achieve the third objective of this utility model, this utility model provides an air circulator, including a rotating mechanical dynamic-static gap sealing structure, wherein the rotating mechanical dynamic-static gap sealing structure is the aforementioned rotating mechanical dynamic-static gap sealing structure.

[0014] A further embodiment is that the air circulator also includes a volute and a fan. The drive shaft of the rotating mechanical dynamic-static clearance sealing structure is rotatably supported inside the volute. The extended end of the drive shaft protrudes from the outside of the volute through the outer through hole. The fan is mounted on the extended end of the drive shaft, and the sealing ring of the rotating mechanical dynamic-static clearance sealing structure is fixedly mounted inside the outer through hole.

[0015] A further embodiment is that the outer through hole has a concave inner surface with a first ring limiting groove and a second ring limiting groove that are connected. The second diameter of the second ring limiting groove is larger than the first diameter of the first ring limiting groove. The outer circumferential end of the sealing ring is embedded in the first ring limiting groove. The air circulator also includes an open retaining ring, which is engaged in the second ring limiting groove and located at the groove opening of the first ring limiting groove adjacent to the second ring limiting groove, so as to restrict the sealing ring in the first ring limiting groove in the axial direction of the drive shaft.

[0016] A further option is that the air circulator also includes an elastic ring, and the outer circumference of the sealing ring has a retaining groove, in which the elastic ring is engaged and abuts against the circumferential surface of the outer through hole.

[0017] A further option is to have a linkage rod fixed inside the drive shaft, which runs along its axial direction to both ends. One end of the linkage rod is threadedly connected to a pressure cap. The fan hub is sleeved on the linkage rod and clamped between the extended end of the drive shaft and the pressure cap.

[0018] Therefore, in the high-speed rotation of the drive shaft, the dynamic and static clearance sealing structure of this utility model provides a dynamic and static clearance between the inner ring hole of the sealing ring and the outer ring wall of the drive shaft. This design avoids friction, wear, and abrasion failures, thereby eliminating abnormal noise and improving the rotational efficiency and stability of the drive shaft. Under the influence of the internal and external pressure difference, the high-pressure gas inside will pass through the dynamic and static gap between the inner ring hole of the sealing ring and the outer ring wall of the drive shaft. The flow is outward. Because the inner ring hole of this invention has multiple square cavities recessed into its circumferential wall, and these cavities are arranged circumferentially and axially within the inner ring hole, the dynamic and static clearances between the inner ring hole's circumferential wall and the outer ring wall of the drive shaft are reduced. High-pressure gas flowing outwards enters each square cavity, and a portion of the airflow near the drive shaft, under the influence of the internal and external pressure difference, flows along the dynamic and static gap between the inner ring hole of the sealing ring and the outer ring wall of the drive shaft. Continuing its high-speed movement towards the low-pressure side, another portion of the airflow near the sealing ring enters multiple square cavities on the periphery of the inner ring bore of the sealing ring. These square cavities divide the high-pressure gas into smaller airflows, creating vortices within the closed square cavities. This generates a strong cross-damping effect, weakening or dissipating the kinetic energy of the high-pressure gas by converting it into internal energy. Simultaneously, some of the airflow within the square cavities flows back to the dynamic and static clearance between the periphery of the inner ring bore of the sealing ring and the outer periphery of the drive shaft. The airflow inside mixes with a portion of the airflow near the drive shaft, thereby compressing this portion of the airflow to increase flow resistance and enhance the sealing effect. Furthermore, each square cavity satisfies a proportionality coefficient. Between 0.17 and 0.21, Let be the cavity depth of the square cavity in the radial direction of the inner annular hole, and let be the side length of each square cavity. The dynamic and static clearance between the inner ring hole of the sealing ring and the outer ring hole of the drive shaft is between 0.5 mm and 3.0 mm. When the gap is between 0.25 mm and 0.45 mm, the amount of gas leakage can be effectively reduced, and the sealing effect can be optimized to further improve the operating efficiency and stability of the air circulator.

[0019] Therefore, the rotating machinery dynamic and static gap sealing structure of this utility model forms a stable non-contact seal between the sealing ring and the transmission shaft to avoid friction and wear, thereby eliminating abnormal noise, improving the rotational efficiency and stability of the transmission shaft, and obtaining a strong damping effect at the dynamic and static gap formed between the sealing ring and the transmission shaft to enhance the sealing effect and effectively reduce gas leakage. Attached Figure Description

[0020] Figure 1 This is a first partial sectional view of an embodiment of the air circulator of this utility model.

[0021] Figure 2 yes Figure 1 Enlarged view at point A.

[0022] Figure 3 This is a partial exploded view of an embodiment of the air circulator of this utility model.

[0023] Figure 4 This is a second partial sectional view of an embodiment of the air circulator of this utility model.

[0024] Figure 5 yes Figure 4 Enlarged view at point B.

[0025] Figure 6 This is a structural diagram of the sealing ring in an embodiment of the air circulator of this utility model.

[0026] Figure 7 This is a schematic diagram of the arrangement of multiple square cavities of the sealing ring in an embodiment of the air circulator of this utility model.

[0027] Figure 8 This is a simulation diagram of the damping effect of multiple square cavities of the sealing ring in an embodiment of the air circulator of this utility model.

[0028] Figure 9 This is a simulation diagram of the leakage flow rate of the dynamic and static gap between the sealing ring and the drive shaft in an embodiment of the air circulator of this utility model.

[0029] The present invention will be further described below with reference to the accompanying drawings and embodiments. Detailed Implementation

[0030] Various exemplary embodiments of the present invention will now be described in detail with reference to the accompanying drawings. The descriptions of the exemplary embodiments are merely illustrative and are in no way intended to limit the present invention or its application or use. The present invention can be implemented in many different forms and is not limited to the embodiments described herein. These embodiments are provided to make the present invention thorough and complete, and to fully express the scope of the present invention to those skilled in the art. It should be noted that, unless otherwise specifically stated, the relative arrangement of components and steps, the composition of materials, numerical expressions, and values ​​set forth in these embodiments should be interpreted as merely exemplary and not as limiting.

[0031] The terms "first," "second," and similar words used in this invention do not indicate any order, quantity, or importance, but are merely used to distinguish different parts. Words such as "including" or "comprising" mean that the element preceding the word encompasses the element listed after it, and do not exclude the possibility of encompassing other elements as well. Terms such as "upper," "lower," "left," and "right" are only used to indicate relative positional relationships; when the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0032] In this invention, when a specific device is described as being located between a first device and a second device, an intermediary device may or may not exist between the specific device and the first or second device. When a specific device is described as being connected to other devices, the specific device may be directly connected to the other devices without an intermediary device, or it may not be directly connected to the other devices but may have an intermediary device.

[0033] All terms used in this invention (including technical or scientific terms) have the same meaning as understood by one of ordinary skill in the art, unless otherwise specifically defined. It should also be understood that terms defined in general dictionaries should be interpreted as having the meaning consistent with their meaning in the context of the relevant art, and not as having an idealized or highly formalized meaning, unless expressly defined herein.

[0034] Techniques, methods, and equipment known to those skilled in the art may not be discussed in detail, but where appropriate, they should be considered part of the specification.

[0035] See Figures 1 to 7 In this embodiment, the air circulator 10 includes a rotating mechanical dynamic-static gap sealing structure, a volute 11, and a fan 13.

[0036] In this embodiment, the rotating machinery dynamic-static clearance sealing structure includes a sealing ring 17 and a drive shaft 12. The drive shaft 12 can rotatably pass through the inner annular hole 172 of the sealing ring 17 around its own axis. The sealing ring 17 is stationary, and there is a dynamic-static clearance between the peripheral wall surface 1721 of the inner annular hole 172 of the sealing ring 17 and the outer peripheral wall surface of the drive shaft 12. The dynamic-static gap Between 0.25 mm and 0.45 mm.

[0037] Furthermore, in this embodiment, the inner annular hole 172 of the sealing ring 17 has a plurality of square cavities 171 recessed into its peripheral wall 1721. These square cavities 171 are arranged circumferentially and axially in the inner annular hole 172, and each square cavity 171 has a side length of... The diameter is between 0.5 mm and 3.0 mm, and each square cavity 171 satisfies the scaling factor. Between 0.17 and 0.21, The cavity depth of the square cavity 171 in the radial direction of the inner annular hole 172.

[0038] Thus, in this embodiment, the drive shaft 12 of the rotating machinery dynamic-static clearance sealing structure is rotatably supported inside the volute 11, and the extended end 121 of the drive shaft 12 extends out of the volute 11 through the outer through hole 111. The fan 13 is disposed on the extended end 121 of the drive shaft 12, and the sealing ring 17 of the rotating machinery dynamic-static clearance sealing structure in this embodiment is fixedly disposed inside the outer through hole 111.

[0039] Therefore, during the high-speed rotation of the drive shaft 12, there is a dynamic and static clearance between the peripheral wall 1721 of the inner ring hole 172 of the sealing ring 17 and the outer peripheral wall of the drive shaft 12. This avoids friction, wear, and abrasion failure, thereby eliminating abnormal noise and improving the rotational efficiency and stability of the drive shaft 12. Under the action of internal and external pressure difference, the high-pressure gas inside will pass through the dynamic and static gap between the inner ring hole 172 of the sealing ring 17 and the outer peripheral wall of the drive shaft 12. The flow is outward. Because the inner annular hole 172 of the sealing ring 17 in this embodiment has multiple square cavities 171 recessed into its peripheral wall 1721, and these cavities are arranged circumferentially and axially in the inner annular hole 172, the dynamic and static clearance between the peripheral wall 1721 of the inner annular hole 172 of the sealing ring 17 and the outer peripheral wall of the drive shaft 12 is reduced. High-pressure gas flowing outward enters each square cavity 171, and the airflow distribution within the square cavity 171 is as follows: Figure 8 As shown, a portion of the airflow near the drive shaft 12, under the influence of the internal and external pressure difference, flows along the dynamic and static gap between the inner annular hole 172 of the sealing ring 17 and the outer peripheral wall of the drive shaft 12. Continuing to move at high speed towards the low-pressure side, another portion of the airflow near the sealing ring 17 enters multiple square cavities 171 on the periphery wall 1721 of the inner ring hole 172 of the sealing ring 17. These square cavities 171 divide the high-pressure gas into multiple smaller airflows, forming vortices within the closed square cavities 171. This generates a strong cross-damping effect, weakening or dissipating the kinetic energy of the high-pressure gas into internal energy. Simultaneously, some of the airflow within the square cavities 171 flows back to the dynamic and static gap between the periphery wall 1721 of the inner ring hole 172 of the sealing ring 17 and the outer periphery wall of the drive shaft 12. The airflow inside mixes with a portion of the airflow near the drive shaft 12, thereby compressing this portion of the airflow to increase flow resistance and enhance the sealing effect. Furthermore, from... Figure 9 As can be seen from this, each square cavity 171 satisfies the scaling factor. Leakage flow ratio , For the leakage flow rate of the non-contact seal with a square cavity 171, The leakage flow rate of the non-contact seal without a square cavity 171 was measured during the experiment. If it is fixed, then the leakage flow rate of the non-contact seal with a square cavity 171 is... When reduced, the leakage flow rate ratio The cells decrease synchronously, so that each square cavity 171 satisfies the scaling factor. Between 0.17 and 0.21, Let be the cavity depth of the square cavity 171 in the radial direction of the inner annular hole 172, and let be the side length of each square cavity 171. The dynamic and static clearance between the inner annular hole 172 of the sealing ring 17 and the outer annular wall of the drive shaft 12 is between 0.5 mm and 3.0 mm. When the diameter is between 0.25 mm and 0.45 mm, the amount of gas leakage can be effectively reduced, and the sealing effect can be optimized to further improve the operating efficiency and stability of the air circulator 10.

[0040] Therefore, in this embodiment, the rotating machinery dynamic and static gap sealing structure forms a stable non-contact seal between the sealing ring 17 and the transmission shaft 12 to avoid friction and wear, thereby eliminating abnormal noise, improving the rotational efficiency and stability of the transmission shaft 12, and obtaining a strong damping effect at the dynamic and static gap formed between the sealing ring 17 and the transmission shaft 12 to enhance the sealing effect and effectively reduce gas leakage.

[0041] To further improve the sealing effect and reduce gas leakage, each square cavity 171 in this embodiment meets the proportionality coefficient. The value is 0.19, so that the cavity depth of the square cavity 171 in the radial direction of the inner annular hole 172 is [value missing]. To achieve the optimal depth and avoid the cavity depth of square cavity 171 Too large or too small will affect the sealing effect.

[0042] To further improve the sealing effect and further reduce gas leakage, in this embodiment, multiple square cavities 171 are arranged at equal intervals in the circumferential direction of the inner annular hole 172, and in this embodiment, multiple square cavities 171 are arranged at equal intervals in the axial direction of the inner annular hole 172.

[0043] More preferably, in this embodiment, the circumferential distance A2 between two adjacent square cavities 171 in the circumferential direction of the inner annular hole 172 is between 0.1 mm and 0.3 mm, and in this embodiment, the axial distance A1 between two adjacent square cavities 171 in the axial direction of the inner annular hole 172 is between 0.1 mm and 0.3 mm.

[0044] In order to securely install the sealing ring 17 in the outer through hole 111 of the volute 11, in this embodiment, the outer through hole 111 has a first ring limiting groove 1111 and a second ring limiting groove 1112 that are connected and recessed in the circumferential surface of the hole. The second diameter of the second ring limiting groove 1112 is larger than the first diameter of the first ring limiting groove 1111. The outer circumferential end of the sealing ring 17 is embedded in the first ring limiting groove 1111. The air circulator 10 also includes an open retaining ring 16, which is engaged in the second ring limiting groove 1112 and located at the groove opening of the first ring limiting groove 1111 adjacent to the second ring limiting groove 1112, so as to restrict the sealing ring 17 in the first ring limiting groove 1111 in the axial direction of the drive shaft 12, thereby securing the sealing ring 17 in the first ring limiting groove 1111, so that a stable non-contact seal is formed between the sealing ring 17 and the drive shaft 12, thereby improving the stability and reliability of the sealing operation.

[0045] Specifically, the air circulator 10 in this embodiment also includes an elastic ring 18. The outer periphery of the sealing ring 17 is provided with a retaining ring groove 173. The elastic ring 18 is engaged in the retaining ring groove 173 and abuts against the circumferential surface of the outer through hole 111 to ensure that the sealing ring 17 will not easily change position in the axial and radial directions of the transmission shaft 12, thereby further improving the sealing effect of the sealing ring 17.

[0046] Furthermore, in this embodiment, a linkage rod 14 is fixedly installed inside the drive shaft 12, extending axially to both ends of the shaft. One end of the linkage rod 14 is threadedly connected to a pressure cover 15. The hub 131 of the fan 13 is sleeved on the linkage rod 14 and clamped between the extended end 121 of the drive shaft 12 and the pressure cover 15. This effectively prevents the fan 13 from axially shifting or coming off, thereby ensuring that the fan 13 does not axially separate during high-speed rotation, thus improving the working stability and reliability of the fan 13.

[0047] The rotating machinery dynamic and static clearance sealing structure of this embodiment is not only applicable to the air circulator 10, but also to various rotating machinery devices, such as shaft seals of rotating turbines, shaft seals of compressors, shaft seals of pump equipment, and main shaft seals of wind turbines.

[0048] The above embodiments are merely preferred examples of this utility model and are not intended to limit the scope of implementation of this utility model. Therefore, all equivalent changes or modifications made to the structure, features and principles of this utility model patent application should be included within the scope of this utility model patent application.

Claims

1. A sealing structure for dynamic and static clearance of rotating machinery, comprising a sealing ring and a drive shaft, wherein the drive shaft rotatably passes through the inner annular hole of the sealing ring about its own axis, the sealing ring is stationary, and there is a dynamic and static clearance between the peripheral wall of the inner annular hole and the outer peripheral wall of the drive shaft. Its features are: The dynamic and static gap Between 0.25 mm and 0.45 mm, a plurality of square cavities are recessed into the periphery of the hole. These square cavities are arranged circumferentially and axially in the inner annular hole, and the side length of each square cavity is [missing information]. The diameter is between 0.5 mm and 3.0 mm, and each of the square cavities satisfies a scaling factor. Between 0.17 and 0.21, The cavity depth of the square cavity in the radial direction of the inner annular hole.

2. The rotating machinery dynamic and static clearance sealing structure according to claim 1, characterized in that: The multiple square cavities are arranged at equal intervals in the circumferential direction of the inner annular hole; And / or, the plurality of said square cavities are arranged at equal intervals along the axial direction of the inner annular hole.

3. The rotating machinery dynamic and static clearance sealing structure according to claim 2, characterized in that: The circumferential distance between two adjacent square cavities in the inner annular hole is between 0.1 mm and 0.3 mm. And / or, the axial spacing between two adjacent square cavities in the inner annular hole is between 0.1 mm and 0.3 mm.

4. The rotating machinery dynamic and static clearance sealing structure according to any one of claims 1 to 3, characterized in that: Each of the square cavities satisfies a proportionality factor. It is 0.

19.

5. A rotating mechanical device, including a sealing structure for the dynamic and static clearances of the rotating machinery, characterized in that: The rotating machinery dynamic and static clearance sealing structure is the rotating machinery dynamic and static clearance sealing structure as described in any one of claims 1 to 4.

6. An air circulator, including a rotating mechanical dynamic-static gap sealing structure, characterized in that: The rotating machinery dynamic and static clearance sealing structure is the rotating machinery dynamic and static clearance sealing structure as described in any one of claims 1 to 4.

7. The air circulator according to claim 6, characterized in that: The air circulator also includes a volute and a fan. The drive shaft of the rotating mechanical dynamic-static clearance sealing structure is rotatably supported in the volute. The extended end of the drive shaft protrudes from the outside of the volute through the outer through hole. The fan is mounted on the extended end of the drive shaft, and the sealing ring of the rotating mechanical dynamic-static clearance sealing structure is fixedly mounted in the outer through hole.

8. The air circulator according to claim 7, characterized in that: The outer through hole has a first annular groove and a second annular groove that are connected to each other on its circumferential surface. The second diameter of the second annular groove is larger than the first diameter of the first annular groove. The outer circumferential end of the sealing ring is embedded in the first ring limiting groove. The air circulator also includes an open retaining ring, which is engaged in the second ring limiting groove and located at the groove opening of the first ring limiting groove adjacent to the second ring limiting groove, so as to restrict the sealing ring in the first ring limiting groove in the axial direction of the transmission shaft.

9. The air circulator according to claim 7, characterized in that: The air circulator also includes an elastic ring. The outer periphery of the sealing ring has a retaining groove. The elastic ring is engaged in the retaining groove and abuts against the circumferential surface of the outer through hole.

10. The air circulator according to claim 7, characterized in that: The drive shaft is fixedly provided with a linkage rod that runs along its axial direction to both ends. One end of the linkage rod is threadedly connected to a pressure cap. The hub of the fan is sleeved on the linkage rod and clamped between the extended end of the drive shaft and the pressure cap.

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