Gas compressor and locking gasket thereof

Abstract

The invention discloses a gas compressor and a locking gasket thereof, and relates to the technical field of gas compressors. The locking gasket comprises a horizontal part and a locking part, during use, the horizontal part is arranged between the bottom surface of the tenon and the bottom surface of the mortise; at least one lug boss; each lug boss is arranged on the horizontal part, and each lug boss has elasticity; when the impeller is used, the highest height of each protruding part in the radial direction of the impeller disc is larger than the distance between the bottom face of the tenon and the bottom face of the mortise. Through the arrangement of the elastic protruding parts, part of energy of vibration of the rotor blade can be absorbed and consumed, and vibration of the rotor blade is reduced. And the contact surfaces of the tenon and the mortise can be clung to each other through the elastic force generated by the convex part, so that the micro motion between the tenon and the mortise is limited. If the fretting generated by the tenon and the mortise is reduced, the fretting wear generated between the tenon and the mortise can be reduced.

Description

Technical Field

[0001] The present application relates to the technical field of compressors, and particularly to a compressor and a locking gasket thereof. Background Art

[0002] During the operation of a gas turbine, due to the combined action of various loads such as centrifugal force and flow channel aerodynamic force, the rotor blades of the compressor will vibrate. If the rotor blades vibrate, it is easy for the tenons and mortises connecting the rotor blades and the impeller disc to slide relative to each other. If the tenons and mortises can slide relative to each other, it is easy for the tenons and mortises to form fretting wear until fatigue cracks initiate. In application scenarios where the impeller disc and the rotor blades are poorly matched, fretting wear will cause premature fatigue failure at the connection of the tenons and mortises, and the service life will be reduced by 35% to 80%.

[0003] It should be clear that the stress magnitude and distribution, fretting frequency, displacement amplitude, surface roughness, and friction coefficient between the contact surfaces of the tenons and mortises are the main factors affecting fretting wear. To control the fretting wear between the tenons and mortises, a common method is to use a metal coating on the contact surfaces of the tenons and mortises, such as silver plating, dry film lubrication, deposition of Ag / Ni metal film, plasma spraying of CuNiIn coating, etc., to reduce the wear of the tenon and mortise substrates by improving the friction coefficient, reducing sliding, or confining fretting within the coating. However, test and usage results show that almost all protective layers (coatings and chemical coatings) will cause varying degrees of reduction in the fatigue strength of the base metal. The reason is that there is no peeling between the coating and the base metal, and cracks initiate and start to propagate in the pores and other defects of the coating under cyclic loading. These cracks cross the bonding surface and enter the surface of the base metal, resulting in a reduction in fatigue strength. That is to say, the anti-fretting wear effect of the coating or plating method is poor. Summary of the Invention

[0004] The purpose of the present application is to provide a compressor and a locking gasket thereof to solve the technical problem that the tenons and mortises in the compressor are prone to fretting wear during use.

[0005] To achieve the above purpose, the present application provides the following technical solutions: In a first aspect, the present application proposes a technical solution for a locking gasket. The locking gasket is applied to a compressor, and the compressor includes an impeller disk and rotor blades; the impeller disk includes a tenon groove, and the rotor blades include tenons; the impeller disk and the rotor blades are tenon-jointed through the tenons and the tenon grooves; the locking gasket includes: a horizontal portion; in use, the horizontal portion is disposed between the bottom surface of the tenon and the bottom surface of the tenon groove; at least one convex portion; each convex portion is disposed on the horizontal portion and each convex portion has elasticity; in use, the maximum height of each convex portion along the radial direction of the impeller disk is greater than the distance between the bottom surface of the tenon and the bottom surface of the tenon groove; the thickness of the convex portion is less than or equal to the thickness of the horizontal portion; and / or, the convex portion is formed by bending the horizontal portion itself; and / or a hollow cavity is provided inside the convex portion.

[0006] As a specific solution in the technical solution of the present application, the maximum heights of the respective convex portions along the radial direction of the impeller disk are equal.

[0007] As a specific solution in the technical solution of the present application, the convex portion is in a strip shape or a dot shape.

[0008] As a specific solution in the technical solution of the present application, the convex portion is in a strip shape; the angular magnitudes of the spatial angles formed by the extending directions of each convex portion and the center line of the horizontal portion are equal; and the spatial angle formed by the extending direction and the center line of the horizontal portion is greater than or equal to 0° and less than or equal to 90°; the center line of the horizontal portion is perpendicular to both the axis line of the impeller disk and the thickness direction of the horizontal portion.

[0009] As a specific solution in the technical solution of the present application, the spatial angle formed by the extending direction and the center line of the horizontal portion is greater than or equal to �0° and less than or equal to 45°.

[0010] As a specific solution in the technical solution of the present application, the extending directions of the respective convex portions are the same.

[0011] As a specific solution in the technical solution of the present application, bending portions are further provided at both ends of the horizontal portion, and after bending, the bending portions limit the relative sliding of the locking gasket and the tenon along the tenon groove.

[0012] As a specific solution in the technical solution of the present application, in use, the length of the horizontal portion in a first direction is greater than or equal to the length of the tenon groove in the first direction; the first direction is parallel to the axis line of the impeller disk; bending portions are further provided at both ends of the horizontal portion; the width of the bending portion in a second direction is greater than the width of the tenon groove in the second direction; the second direction is the circumferential direction of the impeller disk.

[0013] In a second aspect, the present application proposes a technical solution for a compressor, which includes: An impeller disk; the impeller disk includes a disk body; the disk body is provided with a plurality of tenon grooves, and each tenon groove is evenly distributed circumferentially around the disk body; Rotor blades corresponding one-to-one to the tenon grooves; the rotor blades include tenon heads and blade bodies; the tenon heads and the corresponding tenon grooves can form a tenon joint; Locking washers corresponding one-to-one to the tenon grooves, the locking washers being the locking washers described in any one of the first aspect; in use, the locking washers are arranged between the bottom surface of the tenon head and the bottom surface of the tenon groove.

[0014] Compared with the prior art, the beneficial effects of the present application are: By providing the elastic protrusions, the present application can absorb and consume part of the energy of the vibration of the rotor blades, reducing the vibration of the rotor blades. And the elastic force generated by the protrusions can make the contact surfaces of the tenon head and the tenon groove fit tightly, restricting the fretting between the tenon head and the tenon groove. If the fretting generated by the tenon head and the tenon groove is reduced, the fretting wear generated between the tenon head and the tenon groove can be reduced. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 FIG. is a schematic diagram of the assembly of a rotor blade and an impeller disk in the prior art; Figure 2 FIG. is a schematic diagram of the assembly of a rotor blade and an impeller disk proposed in an embodiment of the present application; Figure 3 is Figure 2 an exploded view of the rotor blade and the impeller disk in; Figure 4 FIG. is a three-dimensional schematic diagram of a locking washer proposed in an embodiment of the present application; Figure 5 is Figure 4 a three-dimensional schematic diagram of the bent portion of the locking washer in FIG. after being bent; Figure 6 is Figure 5 a front view schematic diagram of the locking washer in FIG.; Figure 7 FIG. is a three-dimensional schematic diagram of another locking washer proposed in an embodiment of the present application; Figure 8 FIG. is a partial sectional view schematic diagram of a locking washer proposed in an embodiment of the present application; Figure 9 is Figure 6 an enlarged schematic diagram of part A in FIG.; Figure 10 FIG. is a schematic diagram of another locking washer proposed in an embodiment of the present application; Figure 11Schematic diagram of another locking gasket proposed in the embodiments of the present application.

[0016] In the figure: 1. Impeller disc; 11. Disc body; 12. Mortise groove; 121. Bottom surface of the mortise groove; 122. Side surface of the mortise groove; 2. Rotor blade; 21. Tenon; 211. Bottom surface of the tenon; 212. Side surface of the tenon; 22. Blade body; 3. Locking gasket; 31. Horizontal part; 32. Protruding part; 321. Hollow cavity; 33. Bending part. Detailed implementation manners

[0017] Next, the technical solutions in the embodiments of the present application will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present application without creative efforts shall fall within the protection scope of the present application.

[0018] It should be noted that in the description of the present application, the orientation or positional relationship indicated by the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the accompanying drawings. It is only for the convenience of describing the present application and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present application.

[0019] In addition, it should be understood that for the convenience of description, the sizes of the various components shown in the accompanying drawings are not drawn in actual proportional relationships. For example, the thickness or width of some layers may be exaggerated relative to other layers.

[0020] It should be noted that similar reference numerals and letters denote similar items in the following accompanying drawings. Therefore, once an item is defined or described in one accompanying drawing, it will not be necessary to further discuss and describe it specifically in the description of the subsequent accompanying drawings.

[0021] To solve the technical problem of fretting wear that easily occurs between the tenons and mortises in the compressor in the background art, an embodiment of a locking gasket is proposed in this application. Specifically, the locking gasket 3 is applied to the compressor. It should be noted that the structure of the compressor is extremely complex. Since only the impeller disk 1 and the rotor blades 2 in the compressor have the tenon 21 and mortise 12 structures, only the impeller disk 1 and the rotor blades 2 in the compressor are shown in this application, and other components in the compressor are not shown. It does not mean that the compressor in the embodiment of this application only has the impeller disk 1 and the rotor blades 2. It should be understood that the compressor also has other components, but these components are all mature technologies, so they are not shown. The compressor in the prior art includes an impeller disk 1 and a plurality of rotor blades 2 ( Figure 1 only a partial view of the impeller disk 1 and one rotor blade 2 are shown). The impeller disk 1 includes a disk body 11, and a plurality of mortises 12 are provided on the disk body 11, and the respective mortises 12 are evenly distributed circumferentially around the disk body 11. The rotor blades 2 correspond to the mortises 12 one by one, and the rotor blades 2 include tenons 21 and blade bodies 22. The rotor blades 2 can form a tenon joint with the corresponding mortises 12 on the impeller disk 1 through the tenons 21. That is, the rotor blades 2 and the impeller disk 1 form a tenon joint through the tenons 21 and the mortises 12. This is a mature technology and will not be elaborated too much.

[0022] In this embodiment, the locking gasket 3 includes a horizontal portion 31 and at least one protruding portion 32. When in use, the horizontal portion 31 is disposed between the bottom surface 211 of the tenon and the bottom surface 121 of the mortise. As Figure 3 shown, the bottom surface 211 of the tenon is the bottom surface of the tenon 21, and the bottom surface 121 of the mortise is the bottom surface of the mortise 12. As Figures 4 to 11 shown, the respective protruding portions 32 are all disposed on the horizontal portion 31. And each protruding portion 32 has elasticity. When in use, the maximum height of each protruding portion 32 in the radial direction of the impeller disk 1 (that is, the height H as Figure 6 shown) is greater than the distance between the bottom surface 211 of the tenon and the bottom surface 121 of the mortise. That is to say, in this embodiment, the space formed between the locking gasket 3 and the bottom surface 211 of the tenon and the bottom surface 121 of the mortise is an interference fit.

[0023] It should be clear that, in the embodiment of this application, the respective protruding portions 32 can be respectively disposed on opposite sides of the horizontal portion 31, or as Figures 4 to 11 shown, the respective protruding portions 32 are disposed on the same side of the horizontal portion 31.

[0024] In this embodiment, the exploded view of the impeller disk 1, the rotor blades 2, and the locking gasket 3 is as Figure 3 shown, and the assembly drawing of the impeller disk 1, the rotor blades 2, and the locking gasket 3 after being assembled is as Figure 2As shown. Since the maximum height of the protrusion 32 along the radial direction of the impeller disk 1 is greater than the distance between the bottom surface 211 of the tenon and the bottom surface 121 of the mortise groove, and the protrusion 32 is elastic, after assembling the impeller disk 1, the rotor blade 2 and the locking gasket 3 as shown in Figure 2 the protrusion 32 can apply an elastic force along the radial direction of the impeller disk 1 to the tenon 21, and this elastic force causes the contact surfaces of the tenon 21 and the mortise groove 12 (i.e., the side surface 122 of the mortise groove and the side surface 212 of the tenon as shown in Figure 3 ) to be in close contact, that is, to limit the relative displacement (i.e., fretting) between the tenon 21 and the mortise groove 12. And the protrusion 32 with elastic force can absorb and consume part of the vibration energy generated by the rotor blade 2 when the rotor blade 2 vibrates.

[0025] In this embodiment, the locking gasket can absorb and consume part of the energy of the rotor blade vibration through the arrangement of the elastic protrusion, reducing the vibration of the rotor blade. And the elastic force generated by the protrusion can make the contact surfaces of the tenon and the mortise groove in close contact, restricting the fretting between the tenon and the mortise groove. If the fretting generated by the tenon and the mortise groove is reduced, the fretting wear generated between the tenon and the mortise groove can be reduced.

[0026] In the embodiment of the present application, it is only necessary that the tenon 21 and the mortise groove 12 have opposite bottom surfaces 211 of the tenon and 121 of the mortise groove, and there are no restrictions on the shapes and structures of the tenon 21 and the mortise groove 12. For example, the tenon 21 and the mortise groove 12 can be as shown in Figure 3 , or can be the tenons and mortise grooves disclosed in the patent documents with the publication number: CN112324515A, titled: Method for improving the reliability of turbine blades; or, the publication number: CN1013791A, titled: Turbine blade fixing mechanism.

[0027] In the embodiment of the present application, there are no restrictions on the shape and structure of the horizontal portion 31, as long as the horizontal portion 31 can carry the protrusion 32. For example, the horizontal portion 31 can be in the shape of a hollow sheet, or, as shown in Figure 4 and Figure 7 a rectangular sheet, etc.

[0028] In the embodiment of the present application, there are no restrictions on the shape and structure of the protrusion 32, as long as the protrusion 32 can apply an elastic force to the tenon 21. For example, the protrusion 32 can be in the shape of a long strip as shown in Figure 4 and Figure 5 , or can be in the shape of a round dot as shown in Figure 7 .

[0029] In the embodiments of the present application, there are no restrictions on the distribution of the protrusions 32; the only requirement is that the protrusions 32 can apply a uniform elastic force to all portions of the tenon 21. For example, the protrusions 32 can be evenly distributed on the horizontal portion 31. If the protrusions 32 are evenly distributed on the horizontal portion 31, the protrusions 32 can apply a uniform elastic force to all portions of the tenon 21. Of course, in other embodiments, the protrusions 32 can be unevenly distributed to still apply a uniform elastic force to all portions of the tenon 21. Specifically, the distribution of the protrusions 32 can be as shown in the following embodiments.

[0030] Example 1 of distribution of raised portions In this embodiment, if Figure 4 and Figure 5 As shown, the protrusion 32 is in the shape of an elongated strip, and there are two protrusions 32. The extension direction of the two protrusions 32 is parallel to the center line of the horizontal portion 31 (hereinafter referred to as the first center line), and the two protrusions 32 are symmetrical to each other along the first center line. In this embodiment, the center line of the horizontal portion 31 is perpendicular to both the axis of the impeller disk 1 and the thickness direction of the horizontal portion 31 (as shown in FIG. Figure 9 The direction of the thickness D shown is the thickness direction of the horizontal portion 31).

[0031] Example 2 of the distribution of raised parts In this embodiment, if Figure 10 As shown, the protrusion 32 is in the shape of an elongated strip, and there are two protrusions 32. The extension directions of the two protrusions 32 are parallel, and the spatial angle formed by the extension direction and the first center line (that is, as shown in FIG. Figure 10 The included angle θ) shown is greater than 0° and less than or equal to 90°.

[0032] Example 3 of the distribution of raised parts In this embodiment, if Figure 11 As shown, the protrusion 32 is in the shape of an elongated strip, and there are two protrusions 32. Although the two protrusions 32 extend in different directions, they are symmetrical to each other along the first center line. Moreover, the spatial angle formed by the extending direction of the protrusion 32 and the first center line (i.e., Figure 11 The angle α or the angle β shown is greater than 0° and less than or equal to 90°. In this embodiment, the angle α and the angle β are equal.

[0033] So far, the specific embodiment of the protrusion distribution has been introduced.

[0034] It should be clear that Examples 1 to 3 of the present application only list three specific embodiments of the distribution of the protrusions 32. In Examples 1 to 3, each protrusion 32 can apply a uniform elastic force to all parts of the tenon 21. This does not mean that in the present application, the distribution of the protrusions 32 can only be as shown in Examples 1 to 3. It should be understood that since it is impossible to enumerate the distribution of the protrusions 32, Examples 1 to 3 are only illustrative examples of the distribution of the protrusions 32. In the embodiments of the present application, there is no restriction on the number of protrusions 32. For example, the number of protrusions 32 in Examples 1 to 3 can be replaced by three or four, etc.; there is no restriction on the shape and structure of the protrusions 32. For example, the long strip-shaped protrusions 32 in Examples 1 to 3 can be replaced by Figure 7 The dot-shaped protrusions 32 shown are shown.

[0035] As will be seen from the above, in the embodiments of the present application, the spatial angle (i.e., angle θ, angle α, or angle β) formed between the extension direction of the protrusion 32 and the first centerline can be greater than 0° and less than or equal to 90°. If the length of the horizontal portion 31 remains unchanged, the larger the angle, the longer the extension length of the protrusion 32; the longer the extension length of the protrusion 32, the more uniform the elastic force applied by the protrusion 32 to all parts of the tenon 21. As will be seen from the following, if the elongated protrusion 32 is formed by bending or stamping the horizontal portion 31, the smaller the spatial angle, the more difficult it is to form the protrusion 32. To ensure that the protrusion 32 has a sufficient extension length and to facilitate bending or stamping the horizontal portion 31 to form the protrusion 32, in one embodiment of the present application, the spatial angle formed between the extension direction of the protrusion 32 and the centerline of the horizontal portion 31 can be greater than or equal to 30° and less than or equal to 45°. In this embodiment, the spatial angle formed by the extension direction of the protrusion 32 and the center line of the horizontal portion 31 can be any one of 30°, 31°, 32°, 33°, 34°, 35°, 36°, 37°, 38°, 39°, 40°, 41°, 42°, 43°, 44° and 45°, or any degree between two adjacent degrees mentioned above.

[0036] To further facilitate the protrusions 32 applying a uniform elastic force to the tenon 21, in one embodiment of the present application, the maximum heights of the protrusions 32 along the radial direction of the impeller disk 1 can be equal. It should be noted that if the maximum heights of the protrusions 32 along the radial direction of the impeller disk 1 are equal, then after the impeller disk 1, rotor blades 2, and locking washer 3 are assembled, the elastic force applied by each protrusion 32 to the tenon 21 will be substantially uniform, which facilitates uniform elastic force across the tenon 21.

[0037] In an embodiment of the present application, the convex portion 32 may be solid as shown in Figure 8 . In order to make the elastic force formed by the convex portion 32 relatively large, in an embodiment of the present application, as shown in Figure 9 , the thickness of the convex portion 32 (i.e., the thickness d shown in Figure 9 ) may be less than or equal to the thickness of the horizontal portion 31 (i.e., the thickness D shown in Figure 9 ). It should be clear that since the height of the convex portion 32 (i.e., the height H shown in Figure 9 ) is greater than the thickness of the horizontal portion 31 (i.e., the convex portion 32 protrudes from the surface of the horizontal portion 31 in the thickness direction of the horizontal portion 31), if the thickness of the convex portion 32 is less than or equal to the thickness of the horizontal portion 31, then as shown in Figure 9 , a hollow cavity 321 will definitely be formed in the convex portion 32. Compared with the solid convex portion 32, the convex portion 32 with the hollow cavity 321 has better elasticity. In this embodiment, the convex portion 32 with the hollow cavity 321 is also convenient for molding. For example, the horizontal portion 31 can be bent to form the convex portion 32, or the convex portion 32 can be formed by stamping.

[0038] In order to be able to limit the axial movement of the tenon 21 and the mortise 12 along the impeller disk 1, in an embodiment of the present application, bending portions 33 are further provided at both ends of the horizontal portion 31. After the bending portions 33 are bent, they limit the relative sliding of the locking gasket 3 and the tenon 21 along the mortise 12. If the locking gasket 3 and the tenon 21 cannot slide relative to the mortise 12, the fretting wear between the tenon 21 and the mortise 12 can be reduced. In a specific embodiment of the present application, the length of the horizontal portion 31 in the first direction (i.e., the length S shown in Figure 6 ) is greater than or equal to the length of the mortise 12 in the first direction, and the first direction is parallel to the axis of the impeller disk 1. As shown in Figure 4 , bending portions 33 are further provided at both ends of the horizontal portion 31. The width of the bending portion 33 in the second direction is greater than the width of the mortise 12 in the second direction, and the second direction is the circumferential direction of the impeller disk 1.

[0039] In use, the horizontal portion 31 is installed between the tenon 21 and the mortise 12. Since the length of the horizontal portion 31 in the first direction is greater than or equal to the length of the mortise 12 in the first direction, it is beneficial to bend the bent portion 33 until the bent portion 33 is in close contact with the end face of the mortise 12. Since the width of the bent portion 33 in the second direction is greater than the width of the mortise 12 in the second direction, the bent bent portion 33 can interfere with the impeller disk 1, which can not only prevent the locking gasket 3 from having a relative displacement in the axial direction of the impeller disk 1, but also prevent the tenon 21 from having a relative displacement in the axial direction of the impeller disk 1. If the tenon 21 cannot have a relative displacement in the axial direction of the impeller disk 1, the fretting between the tenon 21 and the mortise 12 in the axial direction of the impeller disk 1 can be reduced, that is, the fretting wear generated between the tenon 21 and the mortise 12 can be further reduced.

[0040] In the embodiments of the present application, there is no restriction on the connection manner between the bent portion 33 and the horizontal portion 31, nor is there any restriction on the connection manner between each convex portion 32 and the horizontal portion 31. For example, the bent portion 33 and each convex portion 32 can be fixedly welded or integrally formed with the horizontal portion 31, etc.

[0041] In the embodiments of the present application, there is no restriction on the material of the locking gasket 3. Generally, the operating temperature of the compressor is relatively high. In order to improve the service life of the locking gasket 3, in the embodiments of the present application, the locking gasket 3 can be made of a high-temperature resistant metal material. In order for the locking gasket 3 to be both high-temperature resistant and the formed convex portion 32 to have good elasticity and anti-relaxation performance, in an embodiment of the present application, the material of the locking gasket 3 can be a nickel-based superalloy of type GH4169.

[0042] In the embodiments of the locking gasket proposed in the present application, by providing elastic convex portions, part of the energy of the vibration of the rotor blade can be absorbed and consumed, and the vibration of the rotor blade can be reduced. And the elastic force generated by the convex portion can make the contact surface between the tenon and the mortise fit tightly, restricting the fretting between the tenon and the mortise. If the fretting generated between the tenon and the mortise is reduced, the fretting wear generated between the tenon and the mortise can be reduced.

[0043] After introducing the locking gasket proposed in the embodiments of the present application, the embodiments of a compressor proposed by the present application will be introduced below. In this embodiment, the compressor includes: an impeller disk 1; the impeller disk 1 includes a disk body 11; the disk body 11 is provided with a plurality of tenon grooves 12, and the tenon grooves 12 are evenly distributed around the circumference of the disk body 11. Rotor blades 2 corresponding to the tenon grooves 12 one by one; the rotor blades 2 include tenon heads 21 and blade bodies 22; the tenon heads 21 and the corresponding tenon grooves 12 can form a tenon joint. Locking gaskets corresponding to the tenon grooves 12 one by one, the locking gaskets are the locking gaskets 3 as described in any of the above embodiments; in use, the locking gasket 3 is arranged between the bottom surface 211 of the tenon head and the bottom surface 121 of the tenon groove; the bottom surface 211 of the tenon head is the bottom surface of the tenon head 21; the bottom surface 121 of the tenon groove is the bottom surface of the tenon groove 12.

[0044] In the embodiments of the compressor proposed by the present application, there is a locking gasket. Through the arrangement of the elastic protrusions, the locking gasket can absorb and consume part of the energy of the vibration of the rotor blades, reducing the vibration of the rotor blades. And the elastic force generated by the protrusions can make the contact surface between the tenon head and the tenon groove fit tightly, restricting the fretting between the tenon head and the tenon groove. If the fretting generated between the tenon head and the tenon groove is reduced, the fretting wear generated between the tenon head and the tenon groove can be reduced.

[0045] Although the embodiments of the present application have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principle and spirit of the present application. The scope of the present application is defined by the appended claims and their equivalents.

Claims

1. A locking gasket (3) is applied to a compressor, and the compressor includes an impeller disk (1) and rotor blades (2); the impeller disk (1) includes a tenon groove (12), and the rotor blades (2) include tenons (21); the impeller disk (1) and the rotor blades (2) form a tenon joint through the tenons (21) and the tenon groove (12); characterized in that, The locking gasket (3) includes: A horizontal portion (31); during use, the horizontal portion (31) is disposed between the bottom surface (211) of the tenon and the bottom surface (121) of the mortise groove; At least one protruding portion (32); each protruding portion (32) is disposed on the horizontal portion (31), and each protruding portion (32) has elasticity; during use, the maximum height of each protruding portion (32) along the radial direction of the impeller disc (1) is greater than the spacing between the bottom surface (211) of the tenon and the bottom surface (121) of the mortise groove; the thickness of the protruding portion (32) is less than or equal to the thickness of the horizontal portion (31); and / or, the protruding portion (32) is formed by bending the horizontal portion (31) itself; and / or a hollow cavity (321) is provided inside the protruding portion (32).

2. The locking gasket (3) according to claim 1, characterized in that, The maximum heights of the respective protruding portions (32) along the radial direction of the impeller disc (1) are equal.

3. The locking gasket (3) according to claim 1, characterized in that, The protruding portion (32) is in a strip shape or a dot shape.

4. The locking gasket (3) according to claim 3, characterized in that, The protruding portion (32) is in a strip shape; the angle of the spatial angle formed by the extending direction of each protruding portion (32) and the center line of the horizontal portion (31) is equal; and the spatial angle formed by the extending direction and the center line of the horizontal portion (31) is greater than or equal to 0° and less than or equal to 90°; the center line of the horizontal portion (31) is perpendicular to both the axis line of the impeller disc (1) and the thickness direction of the horizontal portion (31).

5. The locking gasket (3) according to claim 4, characterized in that, The spatial angle formed by the extending direction and the center line of the horizontal portion (31) is greater than or equal to 30° and less than or equal to 45°.

6. The locking gasket (3) according to claim 4, characterized in that, The extending directions of the respective protruding portions (32) are the same.

7. The locking gasket (3) according to any one of claims 1 to 6, characterized in that, Both ends of the horizontal portion (31) are further provided with bending portions (33), and after bending, the bending portions (33) limit the relative sliding of the locking gasket (3) and the tenon (21) along the mortise groove (12).

8. The locking gasket (3) according to claim 7, characterized in that, During use, the length of the horizontal portion (31) in the first direction is greater than or equal to the length of the mortise groove (12) in the first direction; the first direction is parallel to the axis line of the impeller disc (1); both ends of the horizontal portion (31) are further provided with bending portions (33); the width of the bending portion (33) in the second direction is greater than the width of the mortise groove (12) in the second direction; the second direction is the circumferential direction of the impeller disc (1).

9. A compressor, characterized in that, Including: An impeller disc (1); the impeller disc (1) includes a disc body (11); the disc body (11) is provided with a plurality of mortise grooves (12), and the respective mortise grooves (12) are evenly distributed around the circumferential direction of the disc body (11); A rotor blade (2) corresponding to the mortise groove (12) one by one; the rotor blade (2) includes a tenon (21) and a blade body (22); the tenon (21) and the corresponding mortise groove (12) can form a tenon joint; A locking gasket corresponding to the mortise groove (12) one by one, and the locking gasket is the locking gasket (3) as described in any one of claims 1 to 8; during use, the locking gasket (3) is disposed between the bottom surface (211) of the tenon and the bottom surface (121) of the mortise groove.

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