A labyrinth seal structure of flexible deformable parts driven by pressure and rotation speed

Abstract

The present invention relates to the technical field of cylindrical non-contact fluid seals, and discloses a pressure and speed driven flexible deformable member labyrinth seal structure, comprising a rotor and a labyrinth stator member, wherein a group of flexible deformable members are axially arranged on the outer surface of the rotor, a group of labyrinth teeth distributed axially are arranged on the inner surface of the labyrinth stator member, a labyrinth tooth cavity is axially arranged between adjacent labyrinth teeth, a proximal axial section of the flexible deformable member is embedded in and fixed on the rotor, and a distal axial section of the flexible deformable member corresponds to the labyrinth tooth cavity, and under the action of the centrifugal force of the rotor rotation or the pressure of the fluid medium, the distal axial section of the flexible deformable member can extend into the labyrinth tooth cavity, that is, the straight-through labyrinth seal structure is transformed into a double-sided staggered labyrinth seal structure; the present invention solves the problems of high leakage of the straight-through labyrinth seal and difficult disassembly and assembly of the double-sided staggered labyrinth seal by installing the flexible deformable member on the rotor and utilizing the elastic deformation effect of the flexible deformable member and the driving effect of pressure and speed.

Description

Technical Field

[0001] The invention relates to the technical field of cylindrical non-contact fluid sealing, and in particular to a pressure and rotation speed driven flexible deformation piece labyrinth sealing structure. Background Art

[0002] As an important component of large turbine machinery, the sealing performance and reliability of the sealing device are crucial to the production efficiency and operation safety of mechanical equipment. At present, according to whether the seal is in contact with the parts that move relatively to it, it can be divided into contact type and non-contact dynamic seal. Because the contact type dynamic seal is in contact with the relatively moving parts, it is easy to cause friction and even wear between the rotor and the stator during operation. The friction will cause the temperature of the contact surface between the rotor and the stator to rise, resulting in a decrease in the life and performance of the sealing device. At the same time, the friction may even cause the system to vibrate, affecting the safety and reliability of the equipment operation. Therefore, contact dynamic seals are mostly used in low temperature and low speed occasions. As the operation of equipment develops towards high speed and high pressure, non-contact dynamic seals are mostly used in large rotating machinery. Because there is a certain sealing gap between them and the relatively moving parts, a series of problems caused by friction and wear caused by contact can be avoided. They can be used in high speed, high pressure and high temperature occasions.

[0003] As a typical non-contact seal, labyrinth seal is widely used in cylindrical rotating mechanical equipment due to its significant advantages of simple structure and low cost. Labyrinth seal refers to a series of neatly arranged annular sealing teeth constructed near the rotor. Multiple expansion chambers and throttling gaps can be formed between the sealing teeth. When the high-pressure medium flows, the throttling process of the throttling gap (pressure energy is converted into kinetic energy) and the kinetic energy dissipation process (kinetic energy is converted into heat energy) generated by the vortex flow of the expansion chamber due to the formation of complex flow, so that the pressure is gradually reduced to achieve the sealing effect. Specifically, taking a basic sealing unit as an example, when the fluid flows through the sealing tooth gap that becomes smaller instantly in the channel, the pressure drops and the flow rate increases (pressure energy is converted into kinetic energy). At the same time, due to the different pressures on both sides of the sealing tooth, the fluid will appear in a jet shape; when the fluid enters the expansion cavity, the flow channel space becomes larger and the fluid volume increases, which can generate a vortex. At this time, the fluid converts kinetic energy into internal energy (kinetic energy is converted into heat energy) through vortex dissipation, and the pressure is further reduced. When passing through multiple units, the pressure is gradually reduced and finally sealed. Labyrinth seals are mainly divided into three typical structural forms: straight-through type, staggered type and stepped type.

[0004] A straight-through labyrinth seal is a structure in which a series of annular sealing teeth arranged in sequence are directly processed around the rotor to form a series of throttling gaps and expansion cavities between the teeth. The straight-through labyrinth seal is shaped like comb teeth and is widely used due to its simple structure, convenient processing and low cost. However, due to its relatively simple flow path, the energy dissipation is relatively weak when flowing through the throttling gap and expansion cavity, so the leakage of the straight-through labyrinth seal is large. The stepped labyrinth seal is based on the straight-through seal and adds some sealing teeth. Its structural feature is that the shape and arrangement of the sealing teeth form a step shape, which increases the complexity of the flow path and enhances energy dissipation. Therefore, the leakage is slightly reduced compared with the straight-through labyrinth seal, but the processing complexity is higher. The staggered labyrinth seal can also be called a staggered tooth seal. The sealing teeth are arranged in a zigzag shape, and an expansion cavity staggered up and down is formed between the teeth. Therefore, the flow channel formed by the seal is more complex and tortuous than the straight-through and stepped labyrinth seals. When the fluid flows through the staggered flow channel, the flow resistance is greater, the vortex dissipation capacity is stronger, and the pressure energy is converted into more internal energy of the fluid. Therefore, the leakage is smaller than that of the straight-through and stepped labyrinth seals. However, because the staggered teeth are formed by the labyrinth teeth on the rotor and the labyrinth teeth on the stator being staggered along the axial direction, and the upper and lower petal structures are split, it is difficult to disassemble and assemble. Therefore, how to propose a new labyrinth seal that is easy to disassemble and assemble and can enhance the flow resistance and reduce leakage is the main problem that needs to be solved at present. Summary of the invention

[0005] In order to solve the problem of large leakage of straight-through labyrinth seals and difficult disassembly and assembly of double-sided staggered labyrinth seals, the present invention proposes a pressure and speed driven flexible deformation part labyrinth seal structure, which is suitable for shaft end and interstage sealing devices of various large turbine machinery such as gas turbines, steam turbines, compressors, etc.

[0006] The technical solution of the present invention is:

[0007] A pressure and speed driven flexible deformable member labyrinth seal structure, comprising a rotor and a labyrinth stator member, wherein a sealing gap for fluid flow is provided radially between the rotor and the labyrinth stator member;

[0008] A group of flexible deformable parts are installed on the outer surface of the rotor, and the inner surface of the labyrinth stator is provided with labyrinth teeth distributed along the axial direction. A labyrinth tooth cavity is provided axially between adjacent labyrinth teeth. The proximal axial section of the flexible deformable part is embedded in and fixed on the rotor, and the distal axial section of the flexible deformable part extends into the labyrinth tooth cavity. The positive direction of the rotor axis is the direction of axial flow of the fluid, and the distal axial section of the flexible deformable part has an angle B with the rotor axis in the opposite direction. The angle B will change under the action of the centrifugal force of the rotor rotation or the pressure of the fluid medium.

[0009] Furthermore, in the installed state, the distal end point of the distal axis section does not radially extend beyond the inner surface of the labyrinth stator component, and the labyrinth stator component can be directly installed from one end to form a sealing gap with the rotor.

[0010] Furthermore, when the medium is under pressure or the rotor is rotating, the angle B increases, and the distal end point is lifted radially outward and extends into the labyrinth tooth cavity.

[0011] Furthermore, the center line of the labyrinth tooth and the positive direction of the rotor axis have an angle A, and the value range of the angle A is 10-80°, and the preferred value range is 30-60°. The function of the angle is to ensure that the labyrinth tooth is a helical tooth.

[0012] Furthermore, the flexible deformable member is an inner thin plate and an outer thin plate (double-layer thin plate) that are tightly attached in the axial direction and overlapped in the circumferential direction, an inner gap is circumferentially provided between adjacent inner thin plates, an outer gap is circumferentially provided between adjacent outer thin plates, the circumferential width of the inner thin plate is greater than the circumferential width of the outer gap, and the circumferential width of the outer thin plate is greater than the circumferential width of the inner gap.

[0013] Alternatively, the flexible deformation member is a brush filament bundle assembly composed of brush filaments closely arranged in the circumferential direction.

[0014] Furthermore, the proximal axial section of the flexible deformation member is embedded in the rotor by welding.

[0015] Alternatively, a clamping sleeve is provided axially between adjacent flexible deformable members, and the flexible deformable members and the clamping sleeve are arranged in sequence along the axial direction and are clamped by a shaft end nut.

[0016] Design ideas:

[0017] Labyrinth seals are widely used in large rotating machinery, and straight-through labyrinth seals are commonly used as sealing structures due to their simple structure and convenient processing. However, straight-through labyrinth seals have the problem of low flow resistance and high leakage. The subsequently developed staggered labyrinth seals have the excellent characteristics of high flow resistance and low leakage, but because the staggered teeth are formed by staggered arrangement of labyrinth teeth on the rotor and labyrinth teeth on the stator along the axial direction, and the upper and lower petal structures are split, it is difficult to disassemble and assemble. The purpose of the present invention is to provide a flexible deformable part installed on the rotor, using the elastic effect of the flexible deformable part and the driving effect of pressure and speed to form a straight-through labyrinth seal structure under zero speed and zero pressure state, and a staggered labyrinth seal structure under working state, thereby solving the problem of high leakage of straight-through labyrinth seals and difficulty in disassembly and assembly of double-sided staggered labyrinth seals.

[0018] Working principle:

[0019] A labyrinth seal structure of a flexible deformable part driven by pressure and speed. In the installed state, the inclination angle of the flexible deformable part on the rotor is small, and the highest point is lower than the inner surface of the stator. It is a straight-through seal. At this time, the sealing stator can be installed from one side without being made into an upper and lower petal structure, and it is relatively convenient to disassemble and assemble. When in a pressurized state, the pressure energy of the pressurized fluid is converted into kinetic energy before entering the labyrinth tooth chamber through the throttling gap. Then, the fluid with a certain flow rate enters the labyrinth tooth chamber. Due to the obstruction of the inner surface of the flexible deformable part, the fluid will be in a stagnant state. At this time, the flow rate of the fluid on the inner surface of the flexible deformable part is zero and the pressure suddenly increases. The fluid with stagnation pressure continues to flow through the flexible deformable part and the inner surface of the left side of the labyrinth tooth chamber into the space formed by the labyrinth tooth chamber and the outer surface of the flexible deformable part. In the process, local flow resistance will be generated near the inner surface of the left side of the labyrinth tooth chamber, and the pressure will drop. Then, the fluid enters the labyrinth tooth chamber and the outer surface of the flexible deformable part. In the space, the flow channel space becomes larger and the volume of the fluid increases, forming a vortex in the cavity to convert kinetic energy into the internal energy of the fluid, and the pressure decreases again. Therefore, there is a pressure difference between the front and rear of the labyrinth tooth cavity. Under the action of this pressure difference, the flexible deformable part will gradually lift up, and the angle between the flexible deformable part and the opposite direction of the fluid flow will gradually increase. The flexible deformable part extends into the labyrinth tooth cavity, forming a staggered labyrinth seal structure; when in a state of pressure and speed, in addition to the flexible deformable part lifting a certain angle caused by the front and rear pressure difference, since the proximal shaft section of the flexible deformable part is fixed on the rotor and the distal shaft section is in a free state, when the rotor rotates, due to the centrifugal action of the rotor itself, the flexible deformable part will have an outward force and will be lifted to a certain angle, which can also form a staggered labyrinth seal. The staggered labyrinth seal can disperse the kinetic energy of the fluid ejected at high speed through the tooth gap to a large extent, so that the pressure energy can be converted into other forms of energy as much as possible to effectively reduce leakage. When the rotation stops and the pressure is unloaded, the flexible deformable part can be restored to the original angle due to its own elastic action. At this time, the highest point will be lower than the surface of the stator, and the stator can be disassembled from one end. The invention has a straight-through structure in the zero-speed and zero-pressure state, and a double-sided staggered structure in the belt-speed or pressure working state, which not only facilitates disassembly and assembly, but also enhances the flow resistance in the working state, achieving the purpose of low leakage and easy installation of the labyrinth seal.

[0020] The advantages and beneficial effects of the present invention are:

[0021] 1) The present invention can form an adaptive labyrinth seal structure by installing a flexible deformable member on the rotating shaft. After the rotation stops and the pressure is unloaded, the highest point of the flexible deformable member is lower than the inner surface of the stator. The sealed stator can be easily installed from one side without the need to form an upper and lower petal structure. Under the belt speed and pressure state, the flexible deformable member can be gradually lifted to form a double-sided staggered labyrinth seal with low leakage, solving the problems of high leakage of straight-through labyrinth seals and difficult disassembly and assembly of staggered labyrinth seals.

[0022] 2) The flexible deformation member and the clamping sleeve of the present invention are arranged in sequence along the axial direction and are clamped by the shaft end nut, so the disassembly and assembly process is relatively convenient.

[0023] 3) The present invention solves the problems of high leakage of straight-through labyrinth seals and difficulty in disassembly and assembly of double-sided staggered labyrinth seals by installing a flexible deformable member on the rotor and utilizing the elastic deformation effect of the flexible deformable member and the driving effect of pressure and speed. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 This is a three-dimensional structural diagram of a pressure and speed driven flexible deformable member labyrinth seal according to Example 1 of the present invention;

[0025] Figure 2 It is a two-dimensional cross-sectional view of a pressure and speed driven flexible deformable member labyrinth seal structure according to Example 1 of the present invention;

[0026] Figure 3 This is a three-dimensional structural diagram of a pressure and speed driven flexible overlapping double-layer thin plate according to Example 1 of the present invention;

[0027] Figure 4 This is a cross-sectional view of the installation state of a pressure and speed driven flexible deformation member labyrinth seal structure according to Example 1 of the present invention;

[0028] Figure 5 This is a cross-sectional view of a pressure- and speed-driven labyrinth seal of a flexible deformable member under pressure according to Example 1 of the present invention;

[0029] Figure 6 This is a cross-sectional view of a pressure and speed driven labyrinth seal of a flexible deformable member in accordance with Example 1 of the present invention under pressure and speed conditions;

[0030] Figure 7 This is a three-dimensional structural diagram of a pressure and speed driven brush bundle deformation member labyrinth seal according to Example 2 of the present invention;

[0031] Figure 8 This is a schematic diagram of a pressure and speed driven flexible deformation member sleeve compression installation structure according to implementation example 3 of the present invention;

[0032] In the figure: 1. rotor; 2. labyrinth stator; 21. labyrinth tooth; 211. center line; 212. angle A; 22. labyrinth tooth cavity; 23. inner surface; 3. flexible deformation member; 31. proximal axial section; 32. distal axial section; 321. distal axial end point; 33. angle B; 4. sealing gap; 5. double-layer thin plate; 51. inner thin plate; 511. inner gap; 52. outer thin plate; 521. outer gap; 6. brush bundle assembly; 61. brush wire; 71. clamping sleeve; 72. shaft end nut. DETAILED DESCRIPTION

[0033] The implementation of the present invention is further described in detail below in conjunction with the accompanying drawings. Example

[0034] Reference Figure 1 , 2 3. A pressure and speed driven flexible deformable part labyrinth seal structure, a sealing gap 4 for fluid flow is provided between the rotor 1 and the labyrinth stator 2 in the radial direction, the positive direction of the axis of the rotor 1 is the direction of axial flow of the fluid, the inner surface 23 of the labyrinth stator 2 is provided with axially distributed labyrinth teeth 21, the angle A212 between the center line of the labyrinth tooth 21 and the positive direction of the rotor axis is 45°, and a labyrinth tooth cavity 22 is provided between adjacent labyrinth teeth 21 in the axial direction.

[0035] A flexible deformable part 3 is installed on the outer surface of the rotor 1. The flexible deformable part 3 is an inner thin plate 51 and an outer thin plate 52 that are tightly attached along the axial direction and overlapped along the circumferential direction. The proximal axial section 31 of the inner thin plate 51 and the outer thin plate 52 is embedded in the rotor 1 by welding, and the distal axial section 32 of the double-layer thin plate 5 extends into the labyrinth tooth cavity 22.

[0036] There is an inner gap 511 between adjacent inner thin plates 51 in the circumferential direction, and an outer gap 521 is provided between adjacent outer thin plates 52 in the circumferential direction. The circumferential width of the inner thin plate 51 is w i Greater than the circumferential width of the outer gap 521 w 1 , the circumferential width of the outer thin plate 52 w o Greater than the circumferential width of the inner gap 511 w 2 .

[0037] When the double-layer thin plate 5 is deformed, the outer diameter of the double-layer thin plate 5 will change. When the inner thin plate 51 has a circumferential angle due to deformation, the circumferential angle of the adjacent outer thin plate 52 will also change. At this time, the setting of the adjacent outer thin plate 52 can close the circumferential gap of the inner thin plate 51, and the double-layer thin plate 5 can always maintain an axially tight and circumferentially overlapping arrangement to prevent fluid from leaking through the double-layer thin plate 5.

[0038] The flexible deformable member 3 is made of copper, and in other embodiments, any metal material that meets the labyrinth sealing working conditions may be used.

[0039] Reference Figure 4 In the installed state, the distal axial section 32 of the double-layer thin plate 5 on the rotor 1 has a small angle B33 in the opposite direction to the axial centerline of the rotor 1, and the distal axial end point 321 does not radially exceed the inner surface 23 of the labyrinth stator component 2. At this time, it is a straight-through labyrinth seal, and the labyrinth stator component 2 can be directly installed from one end.

[0040] Reference Figure 5A plurality of throttling gaps and a labyrinth tooth cavity 22 are formed between the labyrinth teeth 21, and the labyrinth tooth cavity 22 is divided into a first-stage labyrinth tooth cavity, a second-stage labyrinth tooth cavity and a third-stage labyrinth tooth cavity along the fluid flow direction. p 1 Represents the fluid pressure at the tail of the throttling gap and before entering the labyrinth tooth cavity, p 2 Represents the fluid pressure that enters the labyrinth tooth cavity and rushes into the space formed by the inner thin plate and the rotor. p 3 Represents the fluid pressure in the space formed by the outer thin plate 5 of the labyrinth tooth chamber and the labyrinth tooth chamber 22. Taking the fluid flow in the first-stage labyrinth tooth chamber as an example, when the pressurized fluid flows through the sealing gap and enters the labyrinth tooth chamber, part of the pressure energy is converted into kinetic energy. At this time, there is pressure p 1 When the fluid enters the first-stage labyrinth tooth cavity and rushes into the inner surface of the inner thin plate 51, the fluid is blocked by the inner thin plate 5 and is in a stagnant state. At this time, the fluid flow rate is reduced to zero and the pressure increases suddenly. p 2 > p 1 , then with stagnation pressure p 2 In the process of the fluid flowing to the left inner surface of the first-stage labyrinth tooth cavity and entering the space formed by the labyrinth tooth cavity 22 and the outer thin plate 52, a local flow resistance will be generated near the left inner surface, and the pressure will drop. Then, when entering the space formed by the outer thin plate 52 of the first-stage labyrinth tooth cavity and the labyrinth tooth cavity 22, the volume of the fluid increases due to the enlargement of the flow channel space, and a vortex is formed in the cavity to convert kinetic energy into internal energy of the fluid, and the pressure drops again. Therefore, at this time, the fluid pressure between the first-stage labyrinth tooth cavity and the outer thin plate 52 p 3 < p 2 In the case of different pressure differences between the front and rear of the labyrinth tooth cavity 22, the double-layer thin plate 5 is gradually lifted, and the angle B33 between the double-layer thin plate 5 and the opposite direction of the fluid flow gradually increases until the distal end point 321 of the distal axis section 32 of the double-layer thin plate 5 extends into the labyrinth tooth cavity 22. In this way, a staggered labyrinth seal structure is formed, which can disperse the kinetic energy of the fluid ejected at high speed from the tooth gap to a large extent, so that the pressure energy can be converted into other forms of energy as much as possible, and has high flow resistance and low leakage characteristics.

[0041] Reference Figure 6When the medium is under pressure and the rotor 1 is rotating, in addition to the front and rear pressure difference causing the angle B33 between the double-layer thin plate 5 and the opposite direction of the fluid flow to gradually increase until it extends into the labyrinth tooth cavity 22, because the proximal section 31 of the double-layer thin plate 5 is embedded in the rotor 1 by welding, the distal section 32 is in a free state, so when the rotor rotates, due to the centrifugal effect of the rotor itself, the distal section 32 of the double-layer thin plate 5 has a tendency to move outward. Therefore, at this time, the angle B33 will be raised to a certain height under the centrifugal effect of the rotor, and a staggered labyrinth sealing structure can also be formed.

[0042] When the rotation stops and the pressure is unloaded, the double-layer thin plate 5 can be restored to the angle in the installed state due to its own elastic effect. At this time, the highest point will be lower than the inner surface 23 of the labyrinth stator 2, and the labyrinth stator 2 can be removed from one end. By installing a flexible deformable member on the rotor, a straight-through labyrinth seal structure is realized in the zero-speed and zero-pressure state, and a double-sided staggered labyrinth seal structure is realized in the belt speed or pressure working state, which is convenient for disassembly and assembly, and also enhances the flow resistance in the working state, solving the problems of low flow resistance and high leakage of the existing straight-through labyrinth seal and difficult disassembly and assembly of the staggered labyrinth seal. Example

[0043] Reference Figure 7 The difference between this embodiment and the first embodiment is that the flexible deformable member 3 is a brush bundle assembly 6 composed of brush filaments 61 closely arranged in the circumferential direction. The arrangement of the brush filaments 61 should be sufficient to avoid leakage of the fluid. In this embodiment, the brush filaments 61 are cylindrical, and three brush filaments 61 form a group, which are arranged in an equilateral triangle in the circumferential direction to form a brush bundle assembly 6. Example

[0044] Reference Figure 8 The difference between this embodiment and the previous two embodiments is that a clamping sleeve 71 is provided axially between adjacent flexible deformable members 3, and each flexible deformable member 3 and the clamping sleeve 71 are arranged in sequence along the axial direction and clamped by the shaft end nut 72; in this embodiment, the clamping sleeve-flexible deformable member-clamping sleeve-flexible deformable member-clamping sleeve-flexible deformable member-clamping sleeve are installed in sequence, and finally the clamping nut is matched with the external thread of the shaft end of the sleeve to clamp the above parts, so that the flexible deformable member is fixed on the rotor, and in this way it can be disassembled at any time.

[0045] The contents described in the embodiments of this specification are merely an enumeration of the implementation forms of the inventive concept. The protection scope of the present invention should not be regarded as limited to the specific forms described in the embodiments. The protection scope of the present invention also extends to the equivalent technical means that can be conceived by those skilled in the art based on the inventive concept.

Claims

1. A pressure and speed driven flexible deformable member labyrinth seal structure, comprising a rotor (1) and a labyrinth stator (2), characterized in that: A group of flexible deformable members (3) are axially provided on the outer surface of the rotor (1); a group of labyrinth teeth (21) are axially distributed on the inner surface (23) of the labyrinth stator member (2); a labyrinth tooth cavity (22) is axially provided between adjacent labyrinth teeth (21); a proximal axial section (31) of the flexible deformable member (3) is embedded in and fixed to the rotor (1); a distal axial section (32) of the flexible deformable member (3) corresponds to the labyrinth tooth cavity (22); and under the action of the centrifugal force of the rotor rotation or the pressure of the fluid medium, the distal axial section (32) of the flexible deformable member (3) can extend into the labyrinth tooth cavity (22), that is, the straight-through labyrinth seal structure is transformed into a double-sided staggered labyrinth seal structure; The flexible deformable member (3) is a double-layer thin plate (5) which is tightly attached in the axial direction and overlapped in the circumferential direction, and comprises an inner thin plate (51) and an outer thin plate (52); an inner gap (511) is provided circumferentially between adjacent inner thin plates (51), and an outer gap (521) is provided circumferentially between adjacent outer thin plates (52); the circumferential width of the inner thin plate (51) is greater than the circumferential width of the outer gap (521), and the circumferential width of the outer thin plate (52) is greater than the circumferential width of the inner gap (511).

2. A pressure and speed driven flexible deformable member labyrinth seal structure according to claim 1, characterized in that: A sealing gap (4) for fluid flow is provided radially between the rotor (1) and the labyrinth stator component (2); when the flexible deformable component (3) is installed, a distal end point (321) of a distal section (32) of the flexible deformable component (3) is located within the sealing gap (4) and does not extend beyond an inner surface (23) of the labyrinth stator component (2).

3. A pressure and speed driven flexible deformable member labyrinth seal structure according to claim 1, characterized in that: The center line (211) of the labyrinth tooth (21) and the positive direction of the axis line of the rotor (1) form an angle A (212), and the value range of the angle A (212) is 10 to 80 degrees.

4. A pressure and speed driven flexible deformable member labyrinth seal structure according to claim 1, characterized in that: The proximal shaft section (31) of the flexible deformation member (3) is embedded in the rotor (1) by welding.

5. The pressure and speed driven flexible deformable member labyrinth seal structure according to claim 1, characterized in that: A clamping sleeve (71) is provided axially between adjacent flexible deformable members (3); a group of flexible deformable members (3) and a clamping sleeve (71) are arranged in sequence along the axial direction and are clamped by a shaft end nut (72).

6. The pressure and speed driven flexible deformable member labyrinth seal structure according to claim 1, characterized in that: The flexible deformable member (3) is a brush filament bundle assembly (6) composed of brush filaments (61) closely arranged in the circumferential direction.

7. The pressure and speed driven flexible deformable member labyrinth seal structure according to claim 1, characterized in that: The flexible deformation member (3) is made of metal material or polymer material.

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