Self-adaptive inter-shaft sealing device and working method

Abstract

The invention discloses a self-adaptive inter-shaft sealing device and a working method. The self-adaptive inter-shaft sealing device comprises a runway and an auxiliary runway, the runway and the auxiliary runway are both fixedly installed on the inner rotor, a sealing ring is arranged between the runway and the auxiliary runway, and the sealing ring is in interference fit with the outer rotor; a metal guide rail is arranged in the auxiliary runway and fixedly installed on the inner rotor, a sliding block runway is movably installed on the metal guide rail, metal rubber is installed between the axial end face of the metal guide rail and the axial end face of the sliding block runway, and an o-shaped ring is installed between the radial end face of the metal guide rail and the radial end face of the sliding block runway. A movable auxiliary runway sealing structure is adopted, fluid leakage in different directions can be effectively blocked, the sealing device can conduct self-adaptive adjustment to a certain degree according to actual working conditions, dynamic adjustment is conducted according to the stress condition and relative movement of the sealing face, the contact pressure distribution of the sealing end face is more uniform, and the sealing effect is better. And local excessive wear is avoided.

Description

Technical Field

[0001] This invention belongs to the field of aero-engines, and in particular to an adaptive inter-shaft sealing device and its working method. Background Technology

[0002] Modern aero engines typically employ a dual-shaft structure (inner and outer) to shorten the shaft support distance, reduce structural weight, and lower energy consumption. In some advanced engines, the inner and outer shafts may rotate in opposite directions or in the same direction. An intermediate bearing supports the two shafts, and an inter-shaft seal is installed between them. Currently, grate seals are commonly used for inter-shaft sealing; however, grate seals generate significant leakage, easily leading to reduced aero-engine efficiency and failing to meet the requirements of modern engines. Some scholars have proposed applying film seals to inter-shaft sealing. Currently, the most commonly used inter-shaft seals are end-face film seals and cylindrical film seals.

[0003] The sealing ring in end-face film seals is generally an open ring, mostly made of graphite. When the sealing ring structure is an open ring, the outer diameter of the sealing ring is slightly larger than the inner diameter of the outer rotor before assembly, and the sealing ring and the outer rotor rotate synchronously through an interference fit. Dynamic pressure grooves are usually machined on the metal sealing interface to improve the film bearing capacity. US Patent No. 8967627B2 discloses a sealing ring structure consisting of two rings with a spring installed between them. The spring structure can increase or decrease the force on the sealing ring along the direction to some extent, but the two sealing rings do not rotate synchronously during operation, and the spring may fail. Patent application No. WO2022019878A1 discloses an inter-shaft sealing device that allows for the movement of the metal sealing device; however, the structure of this sealing device is relatively complex and difficult to meet engineering requirements.

[0004] Due to the high rotational speed of the outer rotor and the high internal temperature of the engine, coupled with the open-ring structure of the sealing ring, the contact pressure generated by centrifugal force on the contact surface when the outer rotor and the sealing ring rotate synchronously will be relatively large. This often leads to high friction on the contact surface. When the pressure difference between the high-pressure side and the low-pressure side is relatively small, the open-ring sealing ring may be in a "jammed" state. The installation of the sealing device is random, and direct contact between the sealing ring and the metal sealing end face may occur, resulting in "rubbing." The inner and outer rotors of an aero-engine will experience significant axial movement, far exceeding the reserved sealing gap. When axial movement occurs, the film force in the low-pressure side film gap is often less than the sum of the film force in the high-pressure side film gap and the frictional force between the sealing ring and the outer rotor. This leads to "rubbing" of the low-pressure side sealing end face, causing a decrease in the axial width of the sealing ring and an increase in the sealing gap.

[0005] Patent application CN114215916A discloses a film seal structure for the main bearing cavity of an aero-engine. While the structural components are relatively simple and the structural strength is adequate, during axial movement of the inner and outer rotors or initial installation, when the film gap on the low-pressure side approaches zero, the film force in the low-pressure side gap cannot move the sealing ring towards the high-pressure side, potentially leading to wear. Patent application CN118669185A discloses an improved inter-shaft sealing structure for the main sealing ring, using an open-type sealing ring. This sealing structure can reduce wear on the high-pressure side sealing face to some extent, but it is difficult to ensure that the low-pressure side sealing face does not wear when the rotor moves axially. Summary of the Invention

[0006] The purpose of this invention is to provide an adaptive inter-shaft sealing device and its working method, which solves the problem of severe wear on the low-pressure side sealing end face in the prior art.

[0007] To achieve the above objectives, the present invention employs the following technical solution: An adaptive inter-axle sealing device includes a runway and a sub-runway; Both the runway and the auxiliary runway are fixedly installed on the inner rotor. A sealing ring is provided between the runway and the auxiliary runway, and the sealing ring is interference-fitted with the outer rotor. The secondary track is equipped with a metal guide rail, which is fixedly installed on the inner rotor. A slider track is movably installed on the metal guide rail. Metal rubber is installed between the axial end faces of the metal guide rail and the slider track, and an O-ring is installed between the radial end faces of the metal guide rail and the slider track.

[0008] Furthermore, a spacer sleeve is installed between the runway and the metal guide rail, and the spacer sleeve is fixedly installed on the inner rotor.

[0009] Furthermore, a fixing ring is fixedly installed on the inner rotor, which secures the raceway, the spacer sleeve, and the metal guide rail to the inner rotor.

[0010] Furthermore, the outer diameter of the sealing ring is larger than the inner diameter of the outer rotor.

[0011] Furthermore, a first full-circumference cavity is formed on the inner circumference surface of the sealing ring, and a second full-circumference cavity is formed on the outer circumference surface of the sealing ring.

[0012] Furthermore, the sealing ring is made of graphite.

[0013] Furthermore, a high-pressure side hydrodynamic groove is provided on the sealing end face of the runway, and a low-pressure side hydrodynamic groove is provided on the sealing end face of the slider runway.

[0014] Furthermore, the axial width of the sealing ring is smaller than the axial width of the spacer sleeve.

[0015] Furthermore, the inner diameter of the inner circumference of the slider track is smaller than the outer diameter of the outer circumference of the spacer sleeve.

[0016] A method for operating the adaptive inter-shaft sealing device includes: If the inner and outer rotors move axially, reducing the air film gap between the sealing ring and the slider track, the gas flowing into the gap will increase the air film force in that gap, causing the slider track to move further towards the low-pressure side. The metal rubber will be compressed to generate elastic force until the slider track, the metal rubber, and the O-ring reach axial mechanical equilibrium, and the slider track will no longer move axially. If the inner and outer rotors move axially, the air film gap between the sealing ring and the track will decrease. The air film force in the air film gap between the sealing ring and the track will be greater than the air film force in the air film gap between the sealing ring and the slider track, causing the sealing ring to move towards the low-pressure side to achieve axial balance.

[0017] Compared with the prior art, the present invention has the following beneficial effects: This invention provides an adaptive inter-shaft sealing device and its working method. It employs a movable secondary track composed of a metal guide rail, a sliding track, an O-ring, and metal rubber. The metal guide rail is fixedly mounted on an inner rotor, and the sliding track is movably mounted on the metal guide rail. Metal rubber is installed between the axial end faces of the metal guide rail and the sliding track, and an O-ring is installed between the radial end faces of the metal guide rail and the sliding track. The use of elastic elements such as metal rubber and O-rings not only provides a sealing function but also has a certain buffering and shock absorption function. It can absorb and disperse the vibration and impact experienced by the sealing device during operation, reduce the impact of external interference on the sealing performance, and further enhance the anti-interference capability of the sealing device, enabling it to maintain good performance even in harsh working environments. Both the track and the secondary track are fixedly mounted on the inner rotor, and a sealing ring is placed between the track and the secondary track, with an interference fit between the sealing ring and the outer rotor. Through a reasonable layout, good sealing performance is achieved while maintaining structural compactness, improving the space utilization of the equipment. This invention employs a movable secondary runway sealing structure instead of the traditional single-structure secondary runway. This multi-layered sealing design effectively blocks fluid leakage from different directions. The movable secondary runway design allows the sealing device to adaptively adjust to certain extent according to actual working conditions. When operating conditions such as different pressures, temperatures, or speeds change, the movable secondary runway can flexibly move to better fit the sealing surface and ensure sealing performance. Simultaneously, the movable secondary runway can dynamically adjust according to the stress and relative movement of the sealing surface, resulting in a more uniform contact pressure distribution on the sealing end face. This avoids excessive localized wear, reduces the rate of damage to components of the sealing device, decreases the number of equipment downtimes due to seal failure, ensures the stability and continuity of equipment operation, and ultimately extends the overall service life of the entire sealing device and related equipment, reducing maintenance and operating costs. Attached Figure Description

[0018] To more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of the present invention and should not be regarded as a limitation on the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 This is a schematic diagram of an adaptive inter-shaft sealing device according to the present invention.

[0020] Figure 2 This is a schematic diagram showing the stress on the sealing ring, slider track, metal rubber, and O-ring of the present invention.

[0021] Figure 3 This is a schematic diagram of the sealing ring structure of the present invention.

[0022] Figure 4 This is a schematic diagram of the runway end face structure of the present invention.

[0023] Figure 5 This is a schematic diagram of the end face structure of the slider track of the present invention.

[0024] Figure 6 This is a schematic diagram of the end face structure of the metal guide rail of the present invention.

[0025] Wherein: 1-outer rotor, 2-sealing ring, 3-racetrack, 4-high pressure side fluid dynamic pressure groove, 5-inner rotor, 6-spacing sleeve, 7-low pressure side fluid dynamic pressure groove, 8-fixed ring, 9-metal rubber, 10-metal guide rail, 11-O-ring, 12-slider racetrack. Detailed Implementation

[0026] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The components of the embodiments of the present invention described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0027] Therefore, the following detailed description of the embodiments of the invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the invention without inventive effort are within the scope of protection of the invention.

[0028] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.

[0029] In the description of the embodiments of the present invention, it should be noted that if terms such as "upper," "lower," "horizontal," or "inner" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, or the orientation or positional relationship commonly used when the product of the invention is in use, they are only for the convenience of describing the present invention 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 the present invention. Furthermore, terms such as "first" and "second" are only used to distinguish descriptions and should not be construed as indicating or implying relative importance.

[0030] Furthermore, the use of the term "horizontal" does not imply that the component must be absolutely horizontal, but rather that it can be slightly tilted. For example, "horizontal" simply means that its direction is more horizontal than "vertical," and does not mean that the structure must be completely horizontal, but can be slightly tilted.

[0031] In the description of the embodiments of the present invention, it should also be noted that, unless otherwise explicitly specified and limited, the terms "set," "install," "connect," and "link" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in the present invention according to the specific circumstances.

[0032] The present invention will now be described in further detail with reference to the accompanying drawings: See Figure 1 This invention provides an adaptive inter-shaft sealing device, comprising an outer rotor 1, a sealing ring 2, a raceway 3, an inner rotor 5, a spacer sleeve 6, a fixing ring 8, a metal rubber 9, a metal guide rail 10, an O-ring 11, and a slider raceway 12. These components cooperate to construct an adaptive sealing system that automatically adjusts the sealing gap and sealing force according to the motion state and operating conditions of the inner and outer rotors, thereby achieving efficient and reliable inter-shaft sealing.

[0033] like Figure 3As shown, the sealing ring 2 is an open ring, making it easier to install and remove. The open sealing ring 2 has an interference fit with the outer rotor 1. In its natural state, its outer diameter is larger than the inner diameter of the outer rotor 1, and the opening gap after installation is approximately 0.1 mm. This interference fit and small opening gap design ensures that the sealing ring 2 rotates synchronously with the outer rotor 1 under high temperature and high speed, avoiding sealing failure caused by speed differences. Simultaneously, the small opening gap provides space for the thermal expansion and deformation of the sealing ring 2 during operation, preventing damage due to thermal stress concentration. While ensuring structural strength, a first full-circumference cavity is formed on the inner circumference of the sealing ring 2 to reduce the sealing volume, thereby reducing the contact pressure generated by its own centrifugal effect on the contact surface of the outer rotor, and further reducing the friction between the sealing ring 2 and the outer rotor 1, thus reducing energy loss and wear. A second circumferential cavity is formed on the outer circumference of the sealing ring 2. By changing the gas flow path and pressure distribution, it can offset part of the radial force of the gas on the inner circumference of the sealing ring 2, thereby reducing friction and improving the operating efficiency and reliability of the sealing device. The portion of the sealing ring 2 without the cavity is symmetrical about the cavity, ensuring that the sealing ring 2 is subjected to uniform force during rotation, reducing vibration and noise caused by uneven force, and improving the stability of the sealing device. The size of the cavity area on the inner and outer circumferential surfaces is determined according to the actual working conditions, ensuring that the structural strength of the sealing ring 2 is maintained while reducing friction, so that it will not be damaged due to insufficient strength during long-term operation. The sealing ring 2 is made of graphite material with good wear resistance, high strength, and low coefficient of friction with the outer rotor 1. Graphite material has good self-lubricating properties and can form a lubricating film when rubbing against the outer rotor, reducing friction and wear. Its material properties have better compatibility with the outer rotor 1, which can further reduce the coefficient of friction between the two and improve the sealing effect.

[0034] like Figure 4 As shown, a high-pressure side fluid dynamic pressure groove 4 is provided on the runway 3. The structure of the high-pressure side fluid dynamic pressure groove 4 is designed according to the rotation direction of the inner rotor 5 and the outer rotor 1. When the inner and outer rotors move axially, causing the air film gap h1 between the sealing ring 2 and the runway 3 to decrease, the sealing ring 2 will come into contact with the sealing end face of the runway 3. Due to the presence of the high-pressure side fluid dynamic pressure groove 4, the sealing end face of the runway 3 will generate a large air film force. When the fluid flows in the fluid dynamic pressure groove, the special shape of the fluid dynamic pressure groove will cause a change in the pressure distribution of the fluid, thereby forming an air film force. This air film force prevents the sealing ring 2 from contacting the runway 3, greatly reducing the wear of the sealing end face.

[0035] like Figure 5As shown, a low-pressure side hydrodynamic groove 7 is formed on the sealing end face of the slider track 12. The structure of the low-pressure side hydrodynamic groove 7 is designed according to the rotation direction of the inner and outer rotors. When the inner and outer rotors move axially, the air film gap h2 between the sealing ring 2 and the slider track 12 continuously decreases, and the sealing ring 2 and the slider track 12 will come into contact. If the air film force generated by the gap h2 and the low-pressure side hydrodynamic groove 7 is greater than the sum of the elastic force generated by the axial compression of the metal rubber 9 and the frictional force between the slider track 12 and the O-ring 11, the slider track 12 will move towards the low-pressure side, and the sealing ring 2 and the slider track 12 will not come into contact, thus avoiding wear. When the inner and outer rotors move axially, causing the air film gap h1 to decrease, the distance between the end face of the slider track 12 and the right end face of the sealing ring 2 will increase, and the air film force generated in the air film gap h1 will also increase. If the metal rubber 9 is under compression, the sum of the air film force in the air film gap h2 and the frictional force between the slider track 12 and the O-ring 11 is less than the elastic force between the slider track 12 and the metal rubber 9. Therefore, the slider track 12 will move towards the high-pressure side until it reaches a new axial equilibrium position. Through this dynamic adjustment mechanism, the slider track 12 can automatically adjust its position according to different working conditions, ensuring that the sealing device is always in the optimal sealing state.

[0036] The raceway 3, spacer sleeve 6, metal guide rail 10, and fixing ring 8 are fixedly mounted on the inner rotor 5 and rotate together with the inner rotor 5. The fixing ring 8 fixes the spacer sleeve 6, raceway 3, and metal guide rail 10 to the inner rotor 5, serving a positioning and fastening function, ensuring that the relative positions of each component on the inner rotor are fixed, and avoiding sealing failure caused by loosening of components during rotation. The spacer sleeve 6 separates the raceway 3 from the metal guide rail 10 and the slider raceway 12. The axial width of the spacer sleeve 6 is slightly larger than the axial width of the sealing ring 2, so the sum of the air film gaps h1 and h2 is controlled by tolerance. This allows for flexible adjustment of the sealing gap according to actual working conditions and manufacturing tolerance requirements, improving the adaptability and reliability of the sealing device. The metal guide rail 10, slider raceway 12, O-ring 11, and metal rubber 9 form a movable secondary raceway. Both the raceway 3 and the slider raceway 12 have hydrodynamic pressure grooves to increase the air film force in the air film gaps h1 and h2 and balance the axial load. When the inner and outer rotors move axially, the change in air film force causes the slider track 12 to move on the metal guide rail 10, thereby achieving automatic adjustment of the sealing gap. The outer diameter of the outer circumference of the spacer sleeve 6 is larger than the inner diameter of the inner circumference of the slider track 12, which can play an axial positioning role for the slider track 12 and also restrict the axial movement space of the slider track 12 to a certain extent. This ensures that the slider track 12 can move freely within a certain range to adapt to different working conditions, while preventing its movement range from being too large and causing sealing failure, thus improving the stability and controllability of the sealing device.

[0037] like Figure 2 As shown, a sliding pair is formed between the slider track 12 and the metal guide rail 10. When the axial force of the slider track 12 is unbalanced, it can achieve a certain axial movement on the metal guide rail 10, achieving mechanical balance with the metal rubber 9 and the O-ring 11. When the motion state of the inner and outer rotors changes, the sealing gap and the air film force will also change accordingly, resulting in an imbalance of axial force on the slider track 12. Under the action of this unbalanced force, the slider track 12 will move on the metal guide rail 10, and through interaction with the metal rubber 9 and the O-ring 11, it will eventually reach a new mechanical balance state.

[0038] The end face of the metal guide rail 10 is as follows Figure 6 As shown, the metal rubber 9 is installed between the axial end faces of the slider track 12 and the metal guide rail 10. In its natural state, the metal rubber 9 is not subjected to force. The metal guide rail 10 and the slider track 12 define the adjustment range of the metal rubber 9. When the metal rubber 9 is compressed by the slider track 12, it generates elastic force. This elastic force is one of the important adjusting forces for the axial movement of the slider track 12. It can automatically adjust its size according to the movement of the slider track 12, working together with the air film force and friction to bring the slider track 12 to a balanced position. The metal rubber 9 is not subjected to elastic force during initial installation, ensuring that the slider track 12 can move freely and quickly adapt to changes in operating conditions during the initial startup of the device. When the air film gap h2 is fluid lubricated, the generated air film force is greater than the elastic force of the metal rubber 9 and the friction between the slider track 12 and the O-ring 11, ensuring that the slider track 12 can achieve axial sliding, thereby achieving automatic adjustment of the sealing gap. The O-ring 11 is installed between the slider track 12 and the metal guide rail 10, serving as a secondary seal. During the operation of the sealing device, a small amount of fluid may leak between the slider track 12 and the metal guide rail 10. The O-ring 11 can effectively prevent further leakage of this fluid, improving the overall sealing performance of the sealing device. Simultaneously, axial friction is generated between the O-ring 11 and the slider track 12 as the slider track 12 moves. This friction is also one of the resistances to the axial movement of the slider track 12, and it works in conjunction with the elasticity and film force of the metal rubber 9 to adjust the position of the slider track 12. Furthermore, the metal rubber 9 acts as an axial force compensation agent, and the O-ring 11 also acts as an axial force compensation agent and a secondary seal. These devices all rotate together with the inner rotor 5, enabling the sealing device to achieve efficient self-adaptive sealing.

[0039] The operating method of the adaptive inter-shaft sealing device of the present invention includes: When the sealing device is working, if the inner rotor 5 and the outer rotor 1 move axially, causing the gap h2 between the sealing ring 2 and the slider track 12 to decrease, or if the gap h2 between the sealing ring 2 and the slider track 12 is relatively small and close to 0 during installation, the gas flowing into the gap h2 between the sealing ring 2 and the slider track 12 and the low-pressure side hydrodynamic groove 7 will increase the gas film force in the gap, causing the slider track 12 to move further towards the low-pressure side. The metal rubber 9 will be compressed and generate elastic force until the slider track 12, the metal rubber 9, and the O-ring 11 reach axial mechanical equilibrium, and the slider track 12 will no longer move axially. In the design, it is necessary to ensure that the gas film force generated when the gap h2 is fluid lubricated is always greater than the elastic force of the metal rubber 9. The sum of the frictional forces between the sliding block track 12 and the O-ring 11 is necessary to ensure that the sealing ring 2 does not come into contact with the sliding block track 12 to a certain extent. If the inner rotor 5 and the outer rotor 1 move axially, causing the air film gap h1 between the sealing ring 2 and the track 3 to decrease, or if the air film gap h1 between the sealing ring 2 and the track 3 is relatively small and close to 0 during installation, the air film force in the air film gap h1 between the sealing ring 2 and the track 3 is often greater than the air film force in the air film gap h2 between the sealing ring 2 and the sliding block track 12. This will cause the sealing ring 2 to move towards the low-pressure side to achieve axial balance. In the design, it is necessary to ensure that the air film force in the air film gap h1 is greater than the sum of the air film force in the air film gap h2 and the frictional force between the sealing ring 2 and the outer rotor 1 under each working condition.

[0040] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. An adaptive inter-shaft seal apparatus, comprising: Includes the main runway (3) and the secondary runway; The runway (3) and the sub-runway are both fixedly installed on the inner rotor (5). A sealing ring (2) is provided between the runway (3) and the sub-runway. The sealing ring (2) is interference-fitted with the outer rotor (1). A metal guide rail (10) is provided in the secondary track. The metal guide rail (10) is fixedly installed on the inner rotor (5). A slider track (12) is movably installed on the metal guide rail (10). Metal rubber (9) is installed between the axial end faces of the metal guide rail (10) and the slider track (12). An O-ring (11) is installed between the radial end faces of the metal guide rail (10) and the slider track (12).

2. A self-adapting inter-shaft seal device according to claim 1, wherein, A spacer sleeve (6) is provided between the runway (3) and the metal guide rail (10), and the spacer sleeve (6) is fixedly installed on the inner rotor (5).

3. A self-adapting inter-shaft seal device according to claim 1, wherein, A fixing ring (8) is fixedly installed on the inner rotor (5). The fixing ring (8) fixes the runway (3), the spacer sleeve (6) and the metal guide rail (10) on the inner rotor (5).

4. The self-adapting inter-shaft seal of claim 1, wherein, The outer diameter of the sealing ring (2) is larger than the inner diameter of the outer rotor (1).

5. The self-adapting inter-shaft seal of claim 1, wherein, A first full-circumference cavity is provided on the inner circumference surface of the sealing ring (2), and a second full-circumference cavity is provided on the outer circumference surface of the sealing ring (2).

6. A self-adapting inter-shaft seal device according to claim 1, wherein, The sealing ring (2) is made of graphite.

7. A self-adapting inter-shaft seal device according to claim 1, wherein, The high-pressure side fluid dynamic pressure groove (4) is provided on the sealing end face of the runway (3), and the low-pressure side fluid dynamic pressure groove (7) is provided on the sealing end face of the slider runway (12).

8. The self-adapting inter-shaft seal of claim 1, wherein, The axial width of the sealing ring (2) is smaller than that of the spacer sleeve (6).

9. A self-adapting inter-shaft seal device according to claim 1, wherein, The inner diameter of the inner circumference of the slider track (12) is smaller than the outer diameter of the outer circumference of the spacer sleeve (6).

10. A method of operating the self-adapting inter-shaft seal device of any one of claims 1-9, wherein, include: If the inner rotor (5) and the outer rotor (1) move axially, the air film gap between the sealing ring (2) and the slider track (12) will decrease. The gas flowing into the gap between the sealing ring (2) and the slider track (12) will increase the air film force in the gap, causing the slider track (12) to move further towards the low-pressure side. The metal rubber (9) will be compressed to generate elastic force until the slider track (12), the metal rubber (9) and the O-ring (11) reach axial mechanical balance, and the slider track (12) will no longer move axially. If the inner rotor (5) and the outer rotor (1) move axially, the air film gap between the sealing ring (2) and the track (3) will decrease. The air film force in the air film gap between the sealing ring (2) and the track (3) will be greater than the air film force in the air film gap between the sealing ring (2) and the slider track (12), causing the sealing ring (2) to move towards the low-pressure side to achieve axial balance.

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