An interstage sealing structure for an engine rotor and an engine

Abstract

This invention relates to the field of aero-engine technology, specifically proposing an interstage sealing structure for an engine rotor and an engine. The interstage sealing structure includes: a first-stage rotor, a second-stage rotor, and a sealing ring. One end of the first-stage rotor has a rear-end tooth, and one end of the second-stage rotor has a front-end tooth, which are coaxially meshed with the rear-end tooth. The sealing ring is mounted on the outer circumference of the second-stage rotor via an interference fit, and the outer circumference of the sealing ring has grating teeth. The second-stage rotor has an axial positioning surface, and one end of the sealing ring contacts the axial positioning surface. A boss is provided on the inner side of the sealing ring, which engages with the second-stage rotor and is clamped between the front and rear-end teeth. This design achieves a separate design for the grating teeth and the bladed disk, solving the problem of easy relative displacement between the grating teeth and the bladed disk, thereby avoiding grating tooth wear, reducing maintenance costs, and ensuring the reliability of the connection between the grating teeth and the bladed disk.

Description

Technical Field

[0001] This invention belongs to the field of aero-engine technology, and specifically relates to an interstage sealing structure for an engine rotor and an engine. Background Technology

[0002] The serrated sealing structure is one of the common sealing structures for gas turbine engines. It is not only simple in structure, easy to install and maintain, but also has a good sealing effect. It can meet the high requirements of the aero-engine environment while reducing the cost of use and improving the installation efficiency.

[0003] In existing grate sealing structures, the grate structure is typically integrated with the integral bladed disk. During operation, the grate structure scrapes against the corresponding stator structure, making it highly susceptible to wear and bladed disk failure, resulting in high maintenance costs. Therefore, a separate design is needed to reduce maintenance costs by separating the grate structure from the integral bladed disk in the grate sealing structure. However, the connection reliability between the grate structure and the bladed disk in a separate design is poor, making it highly susceptible to the effects of temperature, pressure loads, and engine vibration during operation. This can cause the grate structure to rotate or shift axially relative to the bladed disk. In particular, when the grate structure rotates, the tangential force generated by friction between the grate structure and the stator structure is much greater than the axial force acting on the grate structure, leading to further wear on the grate structure.

[0004] Therefore, existing grate sealing structures cannot avoid relative displacement between the grate structure and the impeller when the grate and impeller are designed separately. Summary of the Invention

[0005] To address the above problems, this invention proposes an interstage sealing structure for an engine rotor and an engine, wherein the interstage sealing structure for an engine rotor includes:

[0006] The first stage rotor and the second stage rotor are provided with a rear end tooth at one end and a front end tooth at one end, wherein the front end tooth and the rear end tooth are coaxially meshed and connected.

[0007] A sealing ring is installed on the outer circumference of the second-stage rotor by an interference fit, and the outer circumference of the sealing ring is provided with serrations;

[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] The sealing ring has a boss on its inner side, which engages with the second-stage rotor and is held between the front tooth and the rear tooth.

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

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

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

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

[0014] In some specific embodiments, a groove is provided on the tooth tip of the front tooth of the second stage rotor near the sealing ring;

[0015] The groove and the boss are positioned correspondingly and their sizes are compatible.

[0016] The boss is embedded in the groove.

[0017] In some specific embodiments, the bottom of the groove is provided with a first inner rounded corner, the size of which is 0.5 mm or more;

[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 0.5 mm or more.

[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] The boss and the groove are spaced apart on the side away from the first stage rotor;

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

[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 perpendicular to the axial direction of the sealing ring is greater than 1.5 mm.

[0024] In some specific embodiments, under operating conditions, the interference fit 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 tooth with the groove is smaller than the tooth height of the other front teeth.

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

[0027] Compared with existing technologies, the interstage sealing structure of the engine rotor of the present invention has at least the following advantages: The sealing ring is interference-fitted onto the outer periphery of the second-stage rotor, thereby achieving a separate structural design between the sealing ring and the second-stage rotor. Specifically, the axial positioning surface of the second-stage rotor can contact one end of the sealing ring, thus restricting the axial displacement of the grates on the sealing ring relative to the second-stage rotor. Simultaneously, the boss located on the inner side of the sealing ring can engage with the second-stage rotor, further restricting the rotation of the grates on the sealing ring relative to the second-stage rotor. While achieving a separate design for the grates and the impeller, the problem of easy relative displacement between the grates and the impeller in the original invention is solved, thereby avoiding grate wear, reducing maintenance costs, and ensuring the reliability of the connection between the grates and the impeller.

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

[0029] Other features and advantages of the invention will be set forth in the following description, and will be apparent in part from the description, or may be learned by practicing the invention. The objects and other advantages of the invention may be realized and obtained by means of the structures pointed out in the description and the drawings. Attached Figure Description

[0030] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

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

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

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

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

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

[0036] In the figure, 100 is the first stage rotor; 110 is the rear end tooth; 200 is the second stage rotor; 210 is the front end tooth; 211 is the groove; 220 is the cylindrical mating surface; 230 is the axial positioning surface; 300 is the sealing ring; 310 is the grate tooth; and 320 is the boss. Detailed Implementation

[0037] 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, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0038] Reference Figure 1 This invention provides an interstage sealing structure for an engine rotor, comprising: a first-stage rotor 100, a second-stage rotor 200, and a sealing ring 300. 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, which is coaxially meshed with the rear end tooth 110. The sealing ring 300 is mounted on the outer periphery of the second-stage rotor 200 via an interference fit, and the outer periphery of the sealing ring 300 is provided with serrated teeth 310. The second-stage rotor 200 is provided with an axial positioning surface 230, 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, which engages with the second-stage rotor 200 and is clamped between the front end tooth 210 and the rear end tooth 110.

[0039] Specifically, the end face of the rear end of the first-stage rotor 100 is uniformly provided with rear end teeth 110 in the circumferential direction, and the end face of the front end of the second-stage rotor 200 is uniformly provided with front end teeth 210 in the circumferential direction. 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 periphery of the second-stage rotor 200 near the first-stage rotor 100 by an interference fit. The outer periphery of the second-stage rotor 200 is provided with an axial positioning surface 230, which can abut against the end face of the sealing ring 300 away from the first-stage rotor 100. Thus, the sealing ring 300 is blocked by the axial positioning surface 230, which restricts the sealing ring 300 in the axial direction of the second-stage rotor 200, thereby restricting the axial displacement of the grating teeth 310 on the outer periphery of the sealing ring 300 relative to the second-stage rotor 200. Meanwhile, a boss 320 is provided on the inner sidewall 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 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, thereby engaging the sealing ring 300 with the second-stage rotor 200 through the boss 320, restricting the movement of the sealing ring 300 in the circumferential direction of the second-stage rotor 200. Furthermore, the boss 320 is embedded between the front tooth 210 of the corresponding second-stage rotor 200 and the rear tooth 110 of the first-stage rotor 100, thereby restricting the axial movement of the boss 320. It also cooperates with the axial positioning surface 230 on the second-stage rotor 200 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 grate 310 of the sealing ring 300 and the second-stage rotor 200, the problem of relative displacement between the original grate and the impeller is solved. This avoids wear of the grate 310 due to abnormal movement. At the same time, when the grate 310 experiences normal working wear, only the grate 310 needs to be repaired and replaced, which reduces maintenance costs and ensures the reliability of the connection between the grate 310 and the second-stage rotor 200.

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

[0041] Specifically, there are two bosses 320, both of which are set on the inner side wall of the sealing ring 300. The two bosses 320 are symmetrically arranged 180° around the sealing ring 300, which can ensure the symmetry between the two bosses 320 on the sealing ring 300 and thus avoid adverse effects on the rotational balance of the second-stage rotor 200.

[0042] In some specific embodiments of the present invention, reference is made to... Figure 2 A cylindrical mating surface 220 is formed on the outer periphery of the second-stage rotor 200 near 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 disposed on the outer periphery of the end of the second-stage rotor 200 near 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. Thus, the axial positioning surface 230 of the second-stage rotor 200 is formed by the end face of the cylindrical mating surface 220 away from the first-stage rotor 100. The sealing ring 300 is assembled onto the cylindrical mating surface 220 from the end of the second-stage rotor 200 near 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, which can restrict the axial displacement of the grating teeth 310 on the sealing ring 300 relative to the second-stage rotor 200 of the impeller.

[0044] In some specific embodiments of the present invention, reference is made to... Figure 3 A groove 211 is provided on the tooth tip of the front tooth 210 of the second-stage rotor 200 near the sealing ring 300. The groove 211 and the boss 320 are positioned correspondingly and their dimensions are compatible. The boss 320 is embedded in the groove 211.

[0045] Specifically, the groove 211 is formed on the side of the top of one of the front teeth 210 of the second-stage rotor 200 near the first-stage rotor 100, near 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 from the end of the second-stage rotor 200 near the first-stage rotor 100, the boss 320 can slide into the groove 211 when the end face of the sealing ring 300 away from the first-stage rotor 100 abuts against the axial positioning surface 230. This allows the boss 320 to be engaged with the groove 211, completing the installation of the sealing ring 300 on the second-stage rotor 200 and restricting the rotation of the grating teeth 310 on the sealing ring 300 relative to the second-stage rotor 200 of the impeller. Furthermore, after the sealing ring 300 and the second stage rotor 200 are installed, the outer wall of the boss 320 on the side near the first stage rotor 100 is directly opposite the tooth root position of the rear tooth 110 corresponding to the front tooth 210 with the groove 211. The axial positioning surface 230 on the second stage rotor 200 can specifically restrict the sealing ring 300 from moving away from the first stage rotor 100 along the axial direction of the sealing ring 300, while the tooth root of the corresponding rear tooth 110 of the first stage rotor 100 can restrict the sealing ring 300 from moving towards the first stage rotor 100 along the axial direction of the sealing ring 300.

[0046] Furthermore, there are at least two grooves 211, which are respectively set on the tooth tops of two different front teeth 210, and the two grooves 211 are corresponding to the two bosses 320 one by one, to ensure the symmetry of the sealing ring 300 and the second stage rotor 200, and to avoid adverse effects on the rotational balance of the second stage rotor 200.

[0047] In some specific embodiments of the present invention, reference is made to... Figure 1 The bottom of the groove 211 is provided with a first inner rounded corner, the size of which is 0.5 mm or more. The side of the boss 320 away from the first-stage rotor 100 is provided with a second inner rounded corner between it and the inner wall of the sealing ring 300, the size of which is 0.5 mm or more.

[0048] Specifically, the junction 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 with a rounded corner structure, thereby forming a first inner rounded corner at the bottom of the groove 211. The size of this first inner rounded corner is at least 0.5 mm, which can avoid large stress concentration at the bottom of the groove 211 during operation and ensure operational stability. At the same time, the junction between the outer wall of the boss 320 on the side away from the first-stage rotor 100 and the inner wall of the sealing ring 300 is also set with a rounded corner structure, thereby forming a second inner rounded corner between the root of the boss 320 and the inner wall of the sealing ring 300. The size of this second inner rounded corner is also at least 0.5 mm, which can avoid large stress concentration at the root of the boss 320 during operation and ensure operational stability.

[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 provided between the boss 320 and the side of the groove 211 away from the first-stage rotor 100. A gap is also provided 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 side of the boss 320 away from the first stage rotor 100 and the groove wall of the groove 211 away from the first stage rotor 100. This can prevent premature contact between the outer wall of the side of the boss 320 away from the first stage rotor 100 and the groove wall of the groove 211 away from the first stage rotor 100 during assembly, which would prevent the end face of the sealing ring 300 away from the first stage rotor 100 from abutting and fitting with the axial positioning surface 230 on the second stage rotor 200. This ensures that the axial positioning surface 230 can play a sufficient axial positioning role for the sealing ring 300. Meanwhile, the 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 can also prevent interference between the first inner fillet of the boss 320 and the groove 211 or between the groove 211 and the second inner fillet of the boss 320, thereby ensuring operational stability. Furthermore, when the boss 320 is fully inserted into the groove 211, there is also a certain gap between the outer wall of the boss 320 on the side closer to the first-stage rotor 100 and the tooth root of the corresponding rear end tooth 110 of the first-stage rotor 100, thereby preventing interference between the boss 320 and the tooth root of the corresponding rear end tooth 110 of the first-stage rotor 100, 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, reference is made to... Figure 4 The thickness of the boss 320 along the axial direction of the sealing ring 300 is 1.5 mm or more. The width of the boss 320 perpendicular to the axial direction of the sealing ring 300 is 1.5 mm or more.

[0052] Specifically, the thickness of the boss 320 along the axial direction of the sealing ring 300 is at least 1.5 mm, and 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 boss 320 can fully restrict the circumferential rotation of the sealing ring 300.

[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 in the sealing ring 300 and the actual stress conditions. Specifically, 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 in the sealing ring 300 is generally stainless steel.

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

[0055] Specifically, after the sealing ring 300 is installed on the cylindrical mating surface 220 of the second-stage rotor 200 via an interference fit, thus completing the installation between the sealing ring 300 and the second-stage rotor 200, the interference amount between the sealing ring 300 and the second-stage rotor 200 is 0.02 mm to 0.05 mm. The magnitude of this interference amount is determined by meeting the requirements of the engine's extreme operating conditions. That is, under the engine's extreme operating conditions, the interference amount 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, reference is made to... Figure 5 The tooth height of the front tooth 210 with the groove 211 is smaller than that of the other front teeth 210. Specifically, after the groove 211 is formed, a thin wall is formed on both sides of the tooth tip of the corresponding front tooth 210. This thin wall structure may deform or be damaged in the end tooth meshing state. Therefore, by reducing the end tooth height of the front tooth 210 with the groove 211, the thin wall structure is eliminated, and the wall thickness on both sides of the groove is sufficient to withstand the torque transmitted by the end tooth.

[0057] The present invention also provides an engine, comprising: an interstage sealing structure for an engine rotor as described in any of the above specific embodiments. The sealing ring 300 is interference-fitted into the cylindrical mating surface 220 of the second-stage rotor 200, thereby achieving a separate structural design between the grating teeth 310 on the outer periphery of the sealing ring 300 and the second-stage rotor 200 of the impeller, thus reducing maintenance costs when the grating teeth 310 wear. Meanwhile, the axial positioning surface 230 of the second-stage rotor 200 can abut against the end face of the sealing ring 300 away from the first-stage rotor 100, thereby restricting the axial displacement of the grating teeth 310 on the sealing ring 300 relative to the second-stage rotor 200 of the impeller in the direction away from the first-stage rotor 100. The boss 320 provided on the inner sidewall of the sealing ring 300 can engage with the groove 211 on the front tooth 210 of the second-stage rotor 200, thereby further restricting the circumferential rotation of the grating teeth 310 on the sealing ring 300 relative to the second-stage rotor 200. At the same time, the tooth root of the corresponding rear tooth 110 on the first-stage rotor 100 can also restrict the axial displacement of the grating teeth 310 on the sealing ring 300 relative to the second-stage rotor 200 of the impeller in the direction closer to the first-stage rotor 100. While completing the separate design of the grating tooth 310 and the impeller, the problem of relative displacement between the original grating tooth and the impeller was solved, thus avoiding grating tooth wear, reducing maintenance costs and ensuring the reliability of the connection between the grating tooth 310 and the impeller.

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

Claims

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

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

4. The interstage sealing structure of the engine rotor according to claim 1, characterized in that, A groove (211) is provided on the tooth tip of the front tooth (210) of the second stage rotor (200) near the sealing ring (300); The groove (211) and the boss (320) are positioned correspondingly and their sizes are compatible. 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 rounded corner, the size of which is 0.5 mm or more; A second inner radius 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 radius is 0.5 mm or more.

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); The boss (320) and the groove (211) are spaced apart on the side away from the first stage rotor (100); The boss (320) is provided with a gap 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) 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.

8. The interstage sealing structure of the engine rotor according to claim 1, characterized in that, In operation, the interference fit 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 tooth (210) with the groove (211) is smaller than the tooth height of the other front teeth (210).

10. An engine, characterized in that, include: The interstage sealing structure of the engine rotor as described in any one of claims 1 to 8.

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