Interstage sealing structure of engine rotor and engine

Abstract

The invention relates to the technical field of aero-engines, in particular to an inter-stage sealing structure of an engine rotor and an engine, and the inter-stage sealing structure of the engine rotor comprises a first-stage rotor, a second-stage rotor and a sealing ring; one end of the first-stage rotor is provided with rear end teeth, one end of the second-stage rotor is provided with front end teeth, and the front end teeth and the rear end teeth are coaxially meshed and connected; the sealing ring is installed on the periphery of the second-stage rotor in an interference fit mode, and labyrinth teeth are arranged on the periphery of the sealing ring. An axial positioning surface is arranged on the second-stage rotor, and one end of the sealing ring is in contact with the axial positioning surface; a boss is arranged on the inner side of the sealing ring, the boss is connected with the second-stage rotor in a clamped mode, and the boss is clamped between the front end teeth and the rear end teeth. When the split design of the comb teeth and the blade disc is completed, the problem that relative displacement easily occurs between the comb teeth and the blade disc is solved, then abrasion of the comb teeth can be avoided, the maintenance cost is reduced, and the connection reliability between the comb teeth and the blade disc is guaranteed.

Description

Technical Field

[0001] The invention belongs to the technical field of aviation engines, and in particular relates to an interstage sealing structure of an engine rotor and an engine. Background Art

[0002] The comb teeth sealing structure is one of the common sealing structures of gas turbine engines. It is not only simple in structure, easy to install and maintain, but also has good sealing effect. It can reduce the use cost and improve the installation efficiency while meeting the high-demand environment suitable for aircraft engines.

[0003] The comb structure in the existing comb sealing structure is usually designed as an integral part of the blade disc. During operation, the comb structure will scrape against the corresponding stator structure, which can easily cause the blade disc to fail due to wear, and the maintenance cost is high. Therefore, it is necessary to design the comb structure and the integral blade disc in the comb sealing structure separately to reduce the maintenance cost. However, the connection reliability between the comb structure and the blade disc of the split-design comb sealing structure is poor, and it is easily affected by the temperature, pressure load and engine vibration during operation, which causes the comb structure to rotate or axially displace relative to the blade disc. In particular, when the comb structure rotates, the tangential force generated by the friction between the comb structure and the stator structure will be much greater than the axial force acting on the comb structure, which will cause further wear of the comb structure.

[0004] Therefore, it is difficult for the existing comb tooth sealing structure to avoid relative displacement between the comb tooth structure and the blade disk when the comb tooth and the blade disk are designed separately. Summary of the invention

[0005] In view of the above problems, the present invention provides an interstage sealing structure of an engine rotor and an engine, wherein an interstage sealing structure of an engine rotor comprises:

[0006] A first-stage rotor and a second-stage rotor, wherein one end of the first-stage rotor is provided with rear end teeth, and one end of the second-stage rotor is provided with front end teeth, and the front end teeth are coaxially meshed with the rear end teeth;

[0007] A sealing ring is installed on the outer periphery of the second-stage rotor through interference fit, and the outer periphery of the sealing ring is provided with comb teeth;

[0008] The second-stage rotor is provided with an axial positioning surface, and one end of the sealing ring is in contact with the axial positioning surface;

[0009] A boss is arranged on the inner side of the sealing ring, the boss is clamped with the second-stage rotor, and the boss is clamped between the front end teeth and the rear end teeth.

[0010] In some specific embodiments, at least two bosses are provided;

[0011] At least two of the bosses are symmetrically arranged along the circumference of the sealing ring.

[0012] In some specific embodiments, a cylindrical mating surface is provided on the outer circumference of one end of the second-stage rotor close to the first-stage rotor, and the sealing ring is assembled on the cylindrical mating surface;

[0013] The side of the cylindrical matching surface away from the first-stage rotor forms the axial positioning surface.

[0014] In some specific embodiments, a groove is provided on the tooth top of the front end teeth of the second stage rotor on a side close to the sealing ring;

[0015] The groove and the boss are arranged in corresponding positions, and their sizes are adapted to each other;

[0016] The boss is embedded in the groove.

[0017] In some specific embodiments, the bottom of the groove is provided with a first inner fillet, and the size of the first inner fillet is greater than 0.5 mm;

[0018] A second inner fillet is provided between the side of the boss away from the first-stage rotor and the inner wall of the sealing ring, and the size of the second inner fillet is greater than 0.5 mm.

[0019] In some specific embodiments, the depth dimension of the groove along the axial direction of the sealing ring is greater than the thickness dimension of the boss along the axial direction of the sealing ring;

[0020] A gap is provided between the boss and the groove on a side away from the first-stage rotor;

[0021] A gap is set between the boss and the tooth root of the rear end teeth of the first-stage rotor.

[0022] In some specific embodiments, the thickness of the boss along the axial direction of the sealing ring is greater than 1.5 mm;

[0023] The width of the boss in the axial direction perpendicular to the sealing ring is greater than 1.5 mm.

[0024] In some specific embodiments, in the working state, the interference between the sealing ring and the second-stage rotor ranges from 0.02 mm to 0.05 mm.

[0025] In some specific embodiments, the tooth height of the front end tooth with the groove is smaller than the tooth height of other front end teeth.

[0026] An engine based on the same concept includes: an interstage sealing structure of an engine rotor as described in any of the above specific embodiments.

[0027] Compared with the prior art, the interstage sealing structure of the engine rotor of the present invention has at least the following advantages: the sealing ring is installed on the outer periphery of the second-stage rotor by interference fit, thereby realizing the split structural design between the sealing ring and the second-stage rotor. Among them, the axial positioning surface of the second-stage rotor can contact with one end of the sealing ring, thereby limiting the axial displacement of the grate teeth on the sealing ring relative to the second-stage rotor, and at the same time, the boss arranged on the inner side of the sealing ring can be engaged with the second-stage rotor, thereby further limiting the rotation of the grate teeth on the sealing ring relative to the second-stage rotor. While completing the split design of the grate teeth and the blade disk, the problem of relative displacement between the original grate teeth and the blade disk is solved, thereby avoiding the wear of the grate teeth, reducing the maintenance cost, and ensuring the reliability of the connection between the grate teeth and the blade disk.

[0028] Compared with the prior art, the engine of the present invention includes the interstage sealing structure of the engine rotor described above, so it has the same beneficial effects as the interstage sealing structure of the engine rotor described above, so it will not be described in detail here.

[0029] Other features and advantages of the present invention will be described in the following description, and partly become obvious from the description, or be understood by implementing the present invention. The purpose and other advantages of the present invention can be realized and obtained by the structures pointed out in the description and the drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0031] Figure 1 A schematic diagram showing an interstage sealing structure of an engine rotor in an embodiment of the present invention is shown;

[0032] Figure 2 A schematic exploded side view of an interstage sealing structure of an engine rotor in an embodiment of the present invention is shown;

[0033] Figure 3 for Figure 2 A magnified image of A;

[0034] Figure 4 A schematic diagram of a sealing ring in an embodiment of the present invention is shown;

[0035] Figure 5 A schematic cross-sectional view of the meshing of the rear end teeth and the front end teeth in an embodiment of the present invention is shown.

[0036] In the figure, 100, first-stage rotor; 110, rear-end teeth; 200, second-stage rotor; 210, front-end teeth; 211, groove; 220, cylindrical matching surface; 230, axial positioning surface; 300, sealing ring; 310, comb teeth; 320, boss. DETAILED DESCRIPTION

[0037] In order to make the purpose, technical solution and advantages of the embodiments of the present invention clearer, the technical solution in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0038] Reference Figure 1 The present invention provides an interstage sealing structure of an engine rotor, comprising: a first-stage rotor 100, a second-stage rotor 200 and a sealing ring 300. A rear end tooth 110 is provided at one end of the first-stage rotor 100, and a front end tooth 210 is provided at one end of the second-stage rotor 200, and the front end tooth 210 is coaxially meshed with the rear end tooth 110. The sealing ring 300 is installed on the outer periphery of the second-stage rotor 200 by interference fit, and a comb tooth 310 is provided on the outer periphery of the sealing ring 300. An axial positioning surface 230 is provided on the second-stage rotor 200, and one end of the sealing ring 300 contacts the axial positioning surface 230. A boss 320 is provided on the inner side of the sealing ring 300, and the boss 320 is clamped with the second-stage rotor 200, and the boss 320 is clamped between the front end tooth 210 and the rear end tooth 110.

[0039] Specifically, rear end teeth 110 are evenly arranged circumferentially on the end surface of the rear end of the first-stage rotor 100, and front end teeth 210 are evenly arranged circumferentially on the end surface of the front end of the second-stage rotor 200. The rear end teeth 110 of the first-stage rotor 100 and the front end teeth 210 of the second-stage rotor 200 are adapted to each other, so that the first-stage rotor 100 and the second-stage rotor 200 are coaxially meshed and connected through the rear end teeth 110 and the front end teeth 210. The sealing ring 300 is installed on the outer circumference of the end of the second-stage rotor 200 close to the first-stage rotor 100 by interference fit, wherein an axial positioning surface 230 is provided on the outer circumference of the second-stage rotor 200, and the axial positioning surface 230 can abut against the end surface of the sealing ring 300 away from the first-stage rotor 100, so that the sealing ring 300 is blocked by the axial positioning surface 230, and the sealing ring 300 is restricted in the axial direction of the second-stage rotor 200, thereby limiting the axial displacement of the comb teeth 310 on the outer circumference of the sealing ring 300 relative to the second-stage rotor 200. At the same time, a boss 320 is provided on the inner wall of the sealing ring 300. When the sealing ring 300 is installed on the outer periphery of the second-stage rotor 200 and the end face of the sealing ring 300 away from the end of the first-stage rotor 100 abuts against the axial positioning surface 230, the boss 320 can be engaged in the groove 211 of the second-stage rotor 200, so that the sealing ring 300 is engaged with the second-stage rotor 200 through the boss 320, and the movement of the sealing ring 300 in the circumferential direction of the second-stage rotor 200 is restricted. In addition, the boss 320 is embedded between the corresponding front end teeth 210 of the second-stage rotor 200 and the rear end teeth 110 of the first-stage rotor 100, so as to restrict the axial movement of the boss 320, and cooperate with each other through the axial positioning surface 230 on the second-stage rotor 200, so as to further restrict the movement of the sealing ring 300 in the axial direction of the second-stage rotor 200. While completing the separate design of the comb teeth 310 of the sealing ring 300 and the second-stage rotor 200, the problem of relative displacement between the original comb teeth and the blade disk is solved, thereby avoiding wear of the comb teeth 310 due to abnormal movement. At the same time, when the comb teeth 310 have normal working wear, only the comb teeth 310 need to be repaired and replaced separately, which reduces the maintenance cost and ensures the connection reliability between the comb teeth 310 and the second-stage rotor 200.

[0040] In some specific embodiments of the present invention, referring to Figure 4 At least two bosses 320 are provided. At least two bosses 320 are symmetrically arranged along the circumference of the sealing ring 300.

[0041] Specifically, there are two bosses 320, both of which are arranged on the inner wall of the sealing ring 300, and the two bosses 320 are symmetrically arranged at 180° around the circumference of the sealing ring 300, thereby ensuring the symmetry between the two bosses 320 on the sealing ring 300, thereby avoiding adverse effects on the rotational balance of the second-stage rotor 200.

[0042] In some specific embodiments of the present invention, referring to Figure 2 A cylindrical mating surface 220 is formed on the outer circumference of one end of the second-stage rotor 200 close to the first-stage rotor 100, and the sealing ring 300 is installed in the cylindrical mating surface 220 by interference fit. An axial positioning surface 230 is formed on the side of the cylindrical mating surface 220 away from the first-stage rotor 100.

[0043] Specifically, the cylindrical mating surface 220 is arranged on the outer circumference of one end of the second-stage rotor 200 close to the first-stage rotor 100, and the outer diameter of the cylindrical mating surface is smaller than the outer diameter of the axial positioning surface 230, so that the axial positioning surface 230 of the second-stage rotor 200 is formed by the end surface of the cylindrical mating surface 220 on the side away from the first-stage rotor 100, and the sealing ring 300 is assembled on the cylindrical mating surface 220 from the end of the second-stage rotor 200 close to the first-stage rotor 100 until the end surface of the sealing ring 300 away from the first-stage rotor 100 abuts against the axial positioning surface 230, which can limit the axial displacement of the comb teeth 310 on the sealing ring 300 relative to the second-stage rotor 200 of the blade disk.

[0044] In some specific embodiments of the present invention, referring to Figure 3 A groove 211 is provided on the tooth top of the front end tooth 210 of the second stage rotor 200 near the sealing ring 300 . The groove 211 and the boss 320 are arranged in a corresponding position and have sizes that match each other. The boss 320 is embedded in the groove 211 .

[0045] Specifically, the groove 211 is opened on the side of the tooth top of one of the multiple front end teeth 210 on the end face of the second-stage rotor 200 close to the first-stage rotor 100, close to the sealing ring 300. The position and size of the groove 211 are adapted to the boss 320. When the sealing ring 300 is installed on the cylindrical mating surface 220 by the end of the second-stage rotor 200 close to the first-stage rotor 100, until the end face of the sealing ring 300 away from the first-stage rotor 100 abuts against the axial positioning surface 230, the boss 320 can be slid into the groove 211, thereby realizing the clamping connection between the boss 320 and the groove 211, completing the installation of the sealing ring 300 on the second-stage rotor 200, and achieving the purpose of limiting the rotation of the comb teeth 310 on the sealing ring 300 relative to the second-stage rotor 200 of the blade disk. Furthermore, after the installation between the sealing ring 300 and the second-stage rotor 200 is completed, the outer wall of the boss 320 on the side close to the first-stage rotor 100 is directly opposite to the root position of the rear end tooth 110 corresponding to the front end tooth 210 provided with the groove 211, and the axial positioning surface 230 on the second-stage rotor 200 can specifically limit the sealing ring 300 from moving in the axial direction of the sealing ring 300 away from the first-stage rotor 100, while the root of the corresponding rear end tooth 110 of the first-stage rotor 100 can limit the sealing ring 300 from moving in the axial direction of the sealing ring 300 toward the first-stage rotor 100.

[0046] Furthermore, there are at least two grooves 211, and the two grooves 211 are respectively arranged on the tooth tops of two different front end teeth 210, and the two grooves 211 are arranged one-to-one with the two bosses 320, so as to ensure the symmetry between the sealing ring 300 and the second-stage rotor 200 and avoid adversely affecting the rotational balance of the second-stage rotor 200.

[0047] In some specific embodiments of the present invention, referring to Figure 1 The bottom of the groove 211 is provided with a first inner fillet, the size of which is greater than 0.5 mm. A second inner fillet is provided between the side of the boss 320 away from the first-stage rotor 100 and the inner wall of the sealing ring 300, the size of which is greater than 0.5 mm.

[0048] Specifically, the intersection between the groove wall of the groove 211 on the side away from the first-stage rotor 100 and the groove wall at the bottom of the groove 211 is set as a fillet structure, so that a first inner fillet is formed at the groove bottom of the groove 211, and the size of the first inner fillet is at least 0.5 mm, so that a large stress concentration is avoided at the bottom of the groove 211 during operation, and the working stability is ensured. At the same time, the intersection between the outer wall of the boss 320 on the side away from the first-stage rotor 100 and the inner side wall of the sealing ring 300 is also set as a fillet structure, so that a second inner fillet is formed between the root of the boss 320 and the inner side wall of the sealing ring 300, and the size of the second inner fillet is also at least 0.5 mm, so that a large stress concentration is avoided at the root of the boss 320 during operation, and the working stability is ensured.

[0049] In some specific embodiments of the present invention, the depth dimension of the groove 211 along the axial direction of the sealing ring 300 is greater than the thickness dimension of the boss 320 along the axial direction of the sealing ring 300. A gap is set between the boss 320 and the side of the groove 211 away from the first-stage rotor 100. A gap is set between the boss 320 and the tooth root of the rear end tooth 110 of the first-stage rotor 100.

[0050] Specifically, the depth of the groove 211 along the axial direction of the sealing ring 300 is greater than the thickness of the boss 320 along the axial direction of the sealing ring 300, that is, when the boss 320 is fully inserted into the groove 211, there is a certain gap between the outer wall of the boss 320 on the side away from the first-stage rotor 100 and the groove wall of the groove 211 on the side away from the first-stage rotor 100, which can avoid premature contact between the outer wall of the boss 320 on the side away from the first-stage rotor 100 and the groove wall of the groove 211 on the side away from the first-stage rotor 100 during assembly, thereby causing the end face of the sealing ring 300 away from the first-stage rotor 100 to be unable to abut and fit with the axial positioning surface 230 on the second-stage rotor 200, thereby ensuring that the axial positioning surface 230 can fully play an axial positioning role for the sealing ring 300. At the same time, the spacing between the outer wall of the side of the boss 320 away from the first-stage rotor 100 and the groove wall of the side of the groove 211 away from the first-stage rotor 100 can also avoid interference between the boss 320 and the first inner fillet of the groove 211 or between the groove 211 and the second inner fillet of the boss 320, thereby ensuring working stability. In addition, when the boss 320 is fully inserted into the groove 211, there is also a certain spacing between the outer wall of the side of the boss 320 close to the first-stage rotor 100 and the tooth root of the corresponding rear end tooth 110 of the first-stage rotor 100, thereby avoiding interference between the boss 320 and the tooth root of the corresponding rear end tooth 110 of the first-stage rotor 100, and ensuring the normal meshing effect of the first-stage rotor 100 and the second-stage rotor 200.

[0051] In some specific embodiments of the present invention, referring to Figure 4 The thickness of the boss 320 along the axial direction of the sealing ring 300 is greater than 1.5 mm. The width of the boss 320 perpendicular to the axial direction of the sealing ring 300 is greater than 1.5 mm.

[0052] Specifically, the thickness of the boss 320 along the axial direction of the sealing ring 300 is at least 1.5 mm. At the same time, the width of the boss 320 perpendicular to the axial direction of the sealing ring 300 is also at least 1.5 mm, thereby ensuring the structural strength of the boss 320 and ensuring that the circumferential rotation of the sealing ring 300 can be fully restricted by the boss 320.

[0053] It should be noted that the specific design of the structural dimensions of the boss 320 needs to be determined by comprehensively considering the material used for the sealing ring 300 and the actual stress conditions. When the thickness of the boss 320 along the axial direction of the sealing ring 300 and the width perpendicular to the axial direction of the sealing ring 300 are both at least 1.5 mm, the material used for the sealing ring 300 is generally stainless steel.

[0054] In some specific embodiments of the present invention, referring to Figure 1 The interference between the sealing ring 300 and the second-stage rotor 200 ranges from 0.02 mm to 0.05 mm.

[0055] Specifically, when the sealing ring 300 is installed on the cylindrical mating surface 220 of the second-stage rotor 200 through interference fit, the interference between the sealing ring 300 and the second-stage rotor 200 is 0.02 mm to 0.05 mm. The size of the interference is determined by being able to meet the requirements of the extreme working state of the engine. That is, under the extreme working state of the engine, the interference between the sealing ring 300 and the second-stage rotor 200 is 0.02 mm to 0.05 mm.

[0056] In some specific embodiments of the present invention, referring to Figure 5 , the tooth height of the front end tooth 210 with the groove 211 is less than the tooth height of other front end teeth 210. Specifically, after the groove 211 is formed, thin walls are formed on both sides of the tooth top of the corresponding front end tooth 210. The thin wall structure may be deformed or damaged when the end teeth are in meshing state. Therefore, by reducing the end tooth height of the front end tooth 210 with the groove 211, the thin wall structure is eliminated, so that the wall thickness on both sides of the groove is thick enough to withstand the torque transmitted by the end teeth.

[0057] The present invention further provides an engine, comprising: an interstage sealing structure of an engine rotor as described in any of the above specific embodiments, wherein the sealing ring 300 is fitted into the cylindrical mating surface 220 of the second-stage rotor 200 by interference fit, thereby realizing a separate structural design between the comb teeth 310 on the outer periphery of the sealing ring 300 and the second-stage rotor 200 of the blade disk, thereby reducing the maintenance cost when the comb teeth 310 are worn. At the same time, the axial positioning surface 230 of the second-stage rotor 200 can abut against the end surface of the sealing ring 300 away from the first-stage rotor 100, thereby limiting the axial displacement of the comb teeth 310 on the sealing ring 300 relative to the second-stage rotor 200 of the blade disk in the direction away from the first-stage rotor 100, and the boss 320 arranged on the inner side wall of the sealing ring 300 can be engaged with the groove 211 on the front end teeth 210 of the second-stage rotor 200, thereby further limiting the circumferential rotation of the comb teeth 310 on the sealing ring 300 relative to the second-stage rotor 200. At the same time, the tooth roots of the corresponding rear end teeth 110 on the first-stage rotor 100 can also limit the axial displacement of the comb teeth 310 on the sealing ring 300 relative to the second-stage rotor 200 of the blade disk in the direction close to the first-stage rotor 100. While completing the separate design of the comb teeth 310 and the blade disk, the original problem of relative displacement between the comb teeth and the blade disk is solved, thereby avoiding wear of the comb teeth, reducing maintenance costs, and ensuring the reliability of the connection between the comb teeth 310 and the blade disk.

[0058] Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent substitutions for some of the technical features therein; and these modifications or substitutions do not make the essence of the corresponding technical solutions deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. An interstage sealing structure of an engine rotor, characterized in that: include: A first-stage rotor (100) and a second-stage rotor (200), wherein one end of the first-stage rotor (100) is provided with a rear end tooth (110), and one end of the second-stage rotor (200) is provided with a front end tooth (210), and the front end tooth (210) is coaxially meshed with the rear end tooth (110); A sealing ring (300) is installed on the outer periphery of the second-stage rotor (200) by interference fit, and comb teeth (310) are arranged on the outer periphery of the sealing ring (300); An axial positioning surface (230) is provided on the second-stage rotor (200), and one end of the sealing ring (300) is in contact with the axial positioning surface (230); A boss (320) is provided on the inner side of the sealing ring (300), the boss (320) is engaged with the second-stage rotor (200), and the boss (320) is clamped between the front end teeth (210) and the rear end teeth (110).

2. The interstage sealing structure of the engine rotor according to claim 1, characterized in that: At least two bosses (320) are provided; At least two of the bosses (320) are symmetrically arranged along the circumference of the sealing ring (300).

3. The interstage sealing structure of the engine rotor according to claim 1, characterized in that: A cylindrical mating surface (220) is provided on the outer periphery of one end of the second-stage rotor (200) close to the first-stage rotor (100), and the sealing ring (300) is assembled on the cylindrical mating surface (220); The side of the cylindrical matching surface (220) away from the first-stage rotor (100) forms the axial positioning surface (230).

4. The interstage sealing structure of the engine rotor according to claim 1, characterized in that: A groove (211) is provided on the tooth top of the front end tooth (210) of the second-stage rotor (200) on a side close to the sealing ring (300); The groove (211) and the boss (320) are arranged in corresponding positions, and their sizes are adapted to each other; The boss (320) is embedded in the groove (211).

5. The interstage sealing structure of the engine rotor according to claim 4, characterized in that: The bottom of the groove (211) is provided with a first inner fillet, and the size of the first inner fillet is greater than 0.5 mm; A second inner fillet is provided between the side of the boss (320) away from the first-stage rotor (100) and the inner wall of the sealing ring (300), and the size of the second inner fillet is greater than 0.5 mm.

6. The interstage sealing structure of the engine rotor according to claim 4, characterized in that: The depth dimension of the groove (211) along the axial direction of the sealing ring (300) is greater than the thickness dimension of the boss (320) along the axial direction of the sealing ring (300); A gap is provided between the boss (320) and a side of the groove (211) away from the first-stage rotor (100); A gap is provided between the boss (320) and the tooth root of the rear end tooth (110) of the first-stage rotor (100).

7. The interstage sealing structure of the engine rotor according to claim 6, characterized in that: The thickness of the boss (320) in the axial direction of the sealing ring (300) is in the range of 1.5 mm or more; The width of the boss (320) perpendicular to the axial direction of the sealing ring (300) is greater than 1.5 mm.

8. The interstage sealing structure of the engine rotor according to claim 1, characterized in that: In a working state, the interference between the sealing ring (300) and the second-stage rotor (200) ranges from 0.02 mm to 0.05 mm.

9. The interstage sealing structure of the engine rotor according to claim 4, characterized in that: The tooth height of the front end tooth (210) provided with the groove (211) is smaller than the tooth height of the other front end teeth (210).

10. An engine, characterized in that: include: An interstage sealing structure for an engine rotor as claimed in any one of claims 1 to 8.

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