Double-suction type centrifugal pump rotating wheel and anti-abrasion method of double-suction type centrifugal pump rotating wheel

Abstract

The invention discloses a double-suction type centrifugal pump runner which comprises a hub, blades and a vortex inducing structure, and the hub is suitable for being connected with a driving component; the two sets of blades are arranged on the two sides of the axial direction of the hub correspondingly. Each group of blades comprises a plurality of blades, the plurality of blades are uniformly arranged at intervals along the circumferential direction of the hub, a channel for liquid circulation is limited between any two circumferentially adjacent blades, and a turbulent flow area is formed on the radial outer side of the suction surface of each blade; the vortex inducing structure is arranged on the suction surface of the blade and is arranged on the upstream boundary of the turbulent flow area. According to the rotating wheel of the double-suction type centrifugal pump, the vortex inducing structures are arranged on the suction surfaces of the blades, so that fluid energy in an outlet area can be increased, fluid separation conditions are reduced, and abrasion of silt to the blades is relieved. According to the double-suction type centrifugal pump rotating wheel, abrasion formation can be restrained from the source, and the abrasion resistance of the double-suction type centrifugal pump rotating wheel is improved.

Description

Technical Field

[0001] The invention relates to the technical field of hydraulic machinery, in particular to a double-suction centrifugal pump impeller and an anti-wear method for the double-suction centrifugal pump impeller. Background Art

[0002] During the operation of a double-suction centrifugal pump, a separation vortex structure will form in the outlet area of ​​the suction surface of the impeller blade. When a double-suction centrifugal pump is used in a river with a lot of sediment, the separation vortex structure will cause serious local sediment wear and damage to the outlet of the impeller blade due to the sediment carried by the water body, which will greatly reduce the operating efficiency and service life of the double-suction centrifugal pump.

[0003] In the related art, the main methods for improving the anti-silt wear performance of the double-suction centrifugal pump impeller include improving the wear resistance of the blade material, reducing the relative flow velocity of the water flow, optimizing the hydraulic design of the blade, etc. These methods all have certain disadvantages. First, improving the wear resistance of the blade material has the problems of complex process and high cost, and the effect is limited; second, reducing the relative flow velocity of the water flow not only cannot completely prevent the blades from being worn and damaged by silt particles, but also reduces the working performance of the unit; third, optimizing the hydraulic design of the blades is usually only optimized for a specific model of centrifugal pump under the design conditions, but the actual operating conditions and environment of the centrifugal pump are very complex, and the anti-wear effect is not obvious. The above methods only focus on the local wear damage itself, and do not suppress the formation process of local wear damage from the source. Summary of the invention

[0004] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, one object of the present invention is to provide a double-suction centrifugal pump runner and a wear prevention method for the double-suction centrifugal pump runner, which can inhibit the formation of wear from the source and improve the wear resistance of the double-suction centrifugal pump runner.

[0005] The present application proposes a double-suction centrifugal pump impeller, which includes a hub, blades and a vortex-inducing structure, wherein the hub is suitable for connection with a driving component; the blades are provided in two groups, and the two groups of blades are respectively provided on both sides of the axial direction of the hub; each group of blades is constructed in multiple numbers, and the multiple blades are evenly spaced along the circumference of the hub, and a channel for circulating liquid is defined between any two circumferentially adjacent blades, and a turbulence zone is formed on the radial outer side of the suction surface of the blade; the vortex-inducing structure is provided on the suction surface of the blade, and is provided on the upstream boundary of the turbulence zone.

[0006] According to the double-suction centrifugal pump impeller of the present application, since a vortex-inducing structure is provided on the suction surface of the blade, the fluid energy in the outlet area can be increased, the fluid separation can be reduced, and the wear of the blades by mud and sand can be alleviated; the double-suction centrifugal pump impeller of the present application can inhibit the formation of wear from the source and improve the wear resistance of the double-suction centrifugal pump impeller.

[0007] According to some embodiments of the present application, a boundary of the spoiler zone is inclined toward the radial inner side and close to the axial outer edge of the blade.

[0008] According to some embodiments of the present application, the dimensionless parameter of the blade flow direction at the upstream starting point of the spoiler zone boundary is S1, and satisfies 0.2≤S1≤0.4; the angle between the spoiler zone boundary and the flow direction is α, and satisfies 30°≤α≤60°.

[0009] According to some embodiments of the present application, the vortex-inducing structure is configured in multiple numbers, and the multiple vortex-inducing structures are arranged at intervals along the boundary of the spoiler zone.

[0010] According to some embodiments of the present application, one of the plurality of vortex inducing structures is disposed at an upstream starting point of a boundary of the turbulence zone.

[0011] According to some embodiments of the present application, the vortex-inducing structure is constructed as a convex structure, and the equivalent diameter of the vortex-inducing structure is D, and satisfies 2mm≤D≤4mm.

[0012] According to some embodiments of the present application, the distance between two adjacent vortex-inducing structures is W, and satisfies 2D≤W≤4D.

[0013] According to some embodiments of the present application, the distances between two adjacent vortex-inducing structures are equal.

[0014] According to some embodiments of the present application, the vortex-inducing structure is integrally formed with the blade; or the vortex-inducing structure is connected to the blade by welding or bonding.

[0015] The present application also proposes an anti-wear method for a double-suction centrifugal pump impeller, and the anti-wear method is: the above-mentioned vortex-inducing structure is arranged on the suction surface of the blade.

[0016] Additional aspects and advantages of the present invention will be given in part in the following description and in part will be obvious from the following description, or will be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0018] Figure 1 is a partial structural cross-sectional view of a double-suction centrifugal pump impeller according to some embodiments of the present application;

[0019] Figure 2 is a schematic diagram of a blade and a vortex inducing structure according to some embodiments of the present application;

[0020] Figure 3 is a partial schematic diagram of a blade and a vortex inducing structure according to some embodiments of the present application;

[0021] Figure 4 is a physical schematic diagram of a double-suction centrifugal pump impeller according to some embodiments of the present application;

[0022] Figure 5 is a schematic diagram comparing the flow field of a double-suction centrifugal pump impeller according to some embodiments of the present application with that of the prior art;

[0023] Figure 6 It is a schematic diagram comparing the wear of the double-suction centrifugal pump impeller according to some embodiments of the present application and the prior art.

[0024] Reference numerals:

[0025] Blade 1; hub 2; vortex inducing structure 3; cover plate 4;

[0026] spoiler area 11; spoiler area boundary 12;

[0027] Blade axial outer edge 13; blade leading edge 14; blade trailing edge 15; blade streamline 16; blade spanwise bone line 17. DETAILED DESCRIPTION

[0028] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0029] Reference below Figure 1-Figure 3 A double-suction centrifugal pump impeller according to an embodiment of the present invention is described.

[0030] The present application proposes a double-suction centrifugal pump impeller, which includes a hub 2, blades 1 and a vortex-inducing structure 3, wherein the hub 2 is suitable for being connected to a driving component; two groups of blades 1 are provided, and the two groups of blades 1 are respectively provided on both sides of the axial direction of the hub 2; each group of blades 1 is constructed in multiple numbers, and the multiple blades 1 are evenly spaced along the circumference of the hub 2, and a channel for circulating liquid is defined between any two circumferentially adjacent blades 1, and a turbulent flow zone 11 is formed on the radial outer side of the suction surface of the blade 1; the vortex-inducing structure 3 is provided on the suction surface of the blade 1, and is provided on the upstream boundary of the turbulent flow zone 11.

[0031] According to the double-suction centrifugal pump impeller of the present application, the hub 2 can be connected to a driving component and driven by the driving component to rotate, and two sets of blades 1 are respectively arranged on both sides of the axial direction of the hub 2, and are suitable for rotating with the hub 2. When the double-suction centrifugal pump impeller rotates, due to the action of centrifugal force, the liquid flows from the center of the double-suction centrifugal pump impeller to the periphery through the channel between the blades 1; the central pressure of the double-suction centrifugal pump impeller is reduced, and the liquid is continuously attracted to flow in, thereby realizing continuous delivery of the liquid.

[0032] It should be noted that in the double-suction centrifugal pump impeller, the blades have a pressure side and a suction side. The suction side refers to the side of the blade that is subject to suction when the fluid flows, and the pressure side refers to the side of the blade that is subject to pressure when the fluid flows. When the double-suction centrifugal pump impeller operates under high flow conditions, the fluid flowing near the suction surface wall of the blade will gradually slow down and backflow due to the influence of viscosity and adverse pressure gradient, forming a separation vortex structure. Boundary layer separation occurs in the outlet area of ​​the blade suction surface, i.e., the radial outer area of ​​the blade suction surface, forming a flow separation area. Due to the influence of flow velocity and flow direction, the fluid in the flow separation area makes the suction surface of the blade susceptible to wear from the mud and sand carried in the fluid.

[0033] According to the double-suction centrifugal pump impeller of the present application, a turbulence zone 11 is formed on the radial outer side of the suction surface of the blade 1, and the vortex-inducing structure 3 is arranged at the upstream boundary of the turbulence zone 11. When the fluid flows through the suction surface of the blade 1, the vortex-inducing structure 3 will disturb the flow field of the fluid, induce the generation of small-scale vortices, intensify the flow of the mainstream and the boundary layer in the flow separation area, intensify the energy exchange between the mainstream and the boundary layer flow, increase the fluid energy near the wall, and then inhibit and reduce fluid separation, change the flow law of sediment, and reduce the wear of the blade 1 by sediment.

[0034] According to the double-suction centrifugal pump impeller of the present application, since the vortex-inducing structure 3 is provided on the suction surface of the blade 1, the fluid energy in the outlet area of ​​the suction surface of the blade 1 can be increased, the fluid separation can be reduced, and the wear of the blade 1 by the mud and sand can be alleviated; the double-suction centrifugal pump impeller of the present application can inhibit the formation of wear from the source and improve the wear resistance of the double-suction centrifugal pump impeller.

[0035] like Figure 1 As shown, the double-suction centrifugal pump impeller of the present application also includes a cover plate 4, and two cover plates 4 are provided, which are respectively arranged on the circumferential outer sides of the two groups of blades 1. The cover plate 4 forms a water inlet, and the water inlet is directly opposite to the center of the hub 2. The edge of the blade 1 where it connects with the cover plate 4 is the axial outer edge 13 of the blade, the edge of the blade 1 close to the water inlet is the leading edge 14 of the blade, and the edge of the blade away from the water inlet is the trailing edge 15 of the blade. When the double-suction centrifugal pump impeller of the present application is in operation, due to the action of centrifugal force, the pressure at the water inlet of the cover plate 4 is reduced, and the liquid is attracted to flow into the water inlet, and is pushed to the periphery by the blades 1 to continuously transport the liquid. The flow direction of the liquid in the double-suction centrifugal pump impeller is as shown in the figure. Figure 1 shown.

[0036] It should be further explained that the specific speed of the double-suction centrifugal pump impeller targeted by the present application is 150r / min-250r / min. Under this specific speed condition, the flow separation area of ​​the blade generally appears as a triangular-shaped area close to the outlet of the double-suction centrifugal pump impeller. The intersection of the boundary of the flow separation area and the axial outer edge of the blade is located at 20%-40% of the axial outer edge of the blade close to the trailing edge of the blade, and the angle between the boundary of the flow separation area and the fluid flow direction is 30°-60°.

[0037] According to some embodiments of the present application, the spoiler zone boundary 12 is inclined toward the radial inner side close to the blade axial outer edge 13. Figure 2 As shown, the boundary 12 of the spoiler zone is inclined in the radial inner direction close to the axial outer edge 13 of the blade, so that the boundary 12 of the spoiler zone is closer to the boundary of the flow separation area of ​​the blade, which can improve the spoiler effect of the vortex inducing structure 3 on the fluid in the flow separation area.

[0038] In order to facilitate the description of the position of the spoiler zone 11, the present application uses a dimensionless parameter S to express the blade flow position. The dimensionless parameter S refers to the ratio of the length from the starting point to a certain point on any blade streamline 16 to the length of the entire streamline. The starting point is located at the trailing edge 15 of the blade, that is, S=0 corresponds to the trailing edge 15 of the blade, and S=1 corresponds to the leading edge 14 of the blade. For example, S=0.2 means that the arc length from a point along the streamline at the location to the outlet is 20% of the arc length of the corresponding streamline. All points with the same dimensionless parameter on the blade streamline 16 constitute the blade span-wise skeleton line 17.

[0039] Further, according to some embodiments of the present application, the dimensionless parameter of the flow direction of the blade 1 at the upstream starting point of the spoiler zone boundary 12 is S1, and satisfies 0.2≤S1≤0.4; the angle between the spoiler zone boundary 12 and the flow direction is α, and satisfies 30°≤α≤60°. It should be noted that, since the spoiler zone boundary 12 is inclined toward the radial inner side and close to the axial outer edge 13 of the blade, the upstream starting point of the spoiler zone boundary 12 is the intersection of the spoiler zone boundary 12 and the axial outer edge 13 of the blade. In this embodiment, Figure 2 , Figure 3 As shown, the turbulence zone 11 is limited to the above-mentioned range, so that the turbulence zone 11 can overlap with the flow separation area of ​​the blade 1, thereby enhancing the influence of the turbulence effect of the vortex inducing structure 3 on the flow separation area, making the effect of the vortex inducing structure 3 more significant, and being able to effectively reduce the flow separation phenomenon and alleviate the wear of mud and sand.

[0040] According to some embodiments of the present application, the vortex inducing structure 3 is constructed in multiple numbers, and the multiple vortex inducing structures 3 are arranged at intervals along the boundary of the disturbance zone 11. In this embodiment, by setting up multiple vortex inducing structures 3, multiple small-scale vortices can be generated by using the vortex inducing structures 3, which further intensifies the disturbance effect on the mainstream and the boundary layer, intensifies energy exchange, increases the fluid flow rate in the boundary layer, changes the movement law of sediment, and reduces the wear of sediment on the blades 1. It should be noted that the number of vortex inducing structures 3 needs to be reasonably selected based on the structure of the double-suction centrifugal pump impeller and the distribution of the flow separation area; the number should not be too large to avoid the situation where the induced vortex is too strong, which induces wall flow separation by itself and has an adverse effect. In some embodiments, the number of vortex inducing structures 3 is constructed to be 1-3.

[0041] According to some embodiments of the present application, one of the multiple vortex inducing structures 3 is disposed at the upstream starting point of the spoiler zone boundary 12. Figure 2 , Figure 3 As shown, multiple vortex inducing structures 3 are arranged from the upstream starting point of the boundary 12 of the turbulence zone, so that each vortex inducing structure 3 can be arranged upstream of the boundary of the turbulence zone 11, so that the small-scale vortices induced by the vortex inducing structures 3 act on the downstream flow separation area, which can better improve the flow separation situation.

[0042] According to some embodiments of the present application, the vortex inducing structure 3 is constructed as a convex structure, and the equivalent diameter of the vortex inducing structure 3 is D, and satisfies 2mm≤D≤4mm. Figure 3 As shown, setting the size of the vortex-inducing structure 3 to the above range can avoid the adverse effects of the vortex-inducing structure 3 on the hydraulic performance, operational safety and stability of the double-suction centrifugal pump impeller while reducing flow separation.

[0043] According to some embodiments of the present application, the spacing between two adjacent vortex inducing structures 3 is W, and satisfies 2D≤W≤4D. In this embodiment, the spacing of the vortex inducing structures 3 is set to the above range, so that the combined effect of multiple vortex inducing structures 3 can be brought into play, and multiple small-scale vortices can be prevented from suppressing each other when the spacing is too small, and the vortex inducing structures 3 can be prevented from deviating from the upstream boundary when the spacing is too large.

[0044] According to some embodiments of the present application, the spacing between two adjacent vortex inducing structures 3 is equal. In this embodiment, the spacing between two adjacent vortex inducing structures 3 will affect the range of action of the small-scale vortex induced by the vortex inducing structures 3. Setting the spacing equal is more convenient for adjusting the size and layout of the vortex inducing structures 3, so that the overall effect of multiple vortex inducing structures 3 is more effective. In some embodiments, the spacing between two adjacent vortex inducing structures 3 can also be constructed to be unequal, which can be designed specifically according to the flow separation area of ​​the double-suction centrifugal pump impeller.

[0045] According to some embodiments of the present application, the vortex-inducing structure 3 is integrally formed with the blade 1; or the vortex-inducing structure 3 is connected to the blade 1 by welding or bonding. In this embodiment, there are multiple ways to set the vortex-inducing structure 3. It can be integrally formed with the blade 1, which is simple to process and low in cost, and is suitable for the construction of new units; it can be fixed on the surface of the blade 1 by welding or bonding, which is suitable for the construction of new units and also for the renovation of existing pump station units, and has a wider range of applications. The vortex-inducing structure 3 of this embodiment is convenient for improving the application performance of the double-suction centrifugal pump impeller, and is easy to implement and promote.

[0046] The present application also proposes a method for preventing wear of a double-suction centrifugal pump impeller. The method for preventing wear is to set the above-mentioned vortex-inducing structure 3 on the suction surface of the blade 1 .

[0047] According to the anti-wear method of the double-suction centrifugal pump impeller of the present application, a vortex-inducing structure 3 is provided on the suction surface of the blade 1. Since the processing and setting method of the vortex-inducing structure 3 is simple and low-cost, the anti-wear method of the present application can be implemented at low cost and high efficiency; and the anti-wear method of the present application can inhibit the formation of wear from the source, and can improve the anti-wear performance of the double-suction centrifugal pump impeller.

[0048] In order to test the anti-wear performance of the double-suction centrifugal pump impeller of the present application, according to the anti-wear method of the double-suction centrifugal pump impeller of the present application, a vortex-inducing structure 3 is set on the suction surface of the blade 1 to carry out a model experiment.

[0049] like Figure 4 As shown, a double-suction centrifugal pump impeller experimental model is established. A turbulence zone 11 is set on the suction surface of the blade 1, and three vortex-inducing structures 3 are set at the boundary of the turbulence zone 11. Among them, the flow direction position of the intersection of the turbulence zone boundary 12 and the blade axial outer edge 13 is S1=0.3, and the angle between the turbulence zone boundary 12 and the flow direction is S2=45°; the vortex-inducing structure 3 is constructed in a hemispherical shape with a diameter of D=3mm, and the spacing between two adjacent vortex-inducing structures 3 is W=3D=9mm.

[0050] The experimental results are as follows:

[0051] Figure 5 (a) is a flow field observation diagram of the outlet area of ​​the suction surface of the blade 1 of the double-suction centrifugal pump runner prototype without the vortex-inducing structure 3; Figure 5 (b) is a flow field observation diagram of the outlet area of ​​the suction surface of blade 1 of the double-suction centrifugal pump runner model with a vortex-inducing structure 3; Figure 6 (a) is the wear result of the outlet area of ​​the suction surface of the blade 1 of the double-suction centrifugal pump impeller prototype without the vortex-inducing structure 3; Figure 6 (b) is the wear result of the outlet area of ​​the suction surface of blade 1 of the double-suction centrifugal pump impeller model with a vortex-inducing structure 3.

[0052] observe Figure 5 (a) It can be seen that a clear “triangular” flow separation region is formed at the outlet area of ​​the suction surface of blade 1. Figure 5 (a) with Figure 5 (b) It can be seen that Figure 5 The “triangular” flow separation area at the outlet of the suction surface of blade 1 in (b) is significantly reduced; after measurement, the flow control rate (the percentage of flow separation area reduction) reaches 41.1%.

[0053] observe Figure 6 (a) It can be found that a clear “triangular” wear damage area is formed at the outlet area of ​​the suction surface of blade 1. Figure 6 (a) with Figure 6 (b) It can be seen that Figure 6 In (b), the "triangular" wear damage area at the outlet area of ​​the suction surface of blade 1 is significantly reduced; after measurement, the wear inhibition rate of the general wear area at the outlet area of ​​the suction surface of blade 1 is 7.16%, and the wear inhibition rate of the local wear area is 24.91%. Among them, the general wear area refers to the area where wear occurs, and the local wear area refers to the area where the surface coating of blade 1 is completely worn.

[0054] According to the above experimental results, it can be concluded that the vortex-inducing structure 3 of the present application can reduce flow separation, effectively inhibit and weaken the wear damage in the outlet area of ​​the suction surface of the blade 1; the double-suction centrifugal pump impeller of the present application has good anti-wear performance.

[0055] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0056] In the description of the present invention, "first feature" or "second feature" may include one or more of the features.

[0057] In the description of the present invention, "plurality" means two or more.

[0058] In the description of the present invention, a first feature being “on” or “under” a second feature may include that the first and second features are directly in contact with each other, or may include that the first and second features are not in direct contact with each other but are in contact with each other via another feature therebetween.

[0059] In the description of the present invention, “on”, “over” and “above” a first feature from a second feature includes the first feature being directly above and obliquely above the second feature, or simply means that the first feature is horizontally higher than the second feature.

[0060] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0061] Although the embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A double-suction centrifugal pump impeller, characterized in that: include: A wheel hub, the wheel hub being adapted to be connected to a driving component; Blades, wherein the blades are provided in two groups, and the two groups of blades are respectively provided on both sides of the hub in the axial direction; each group of blades is constructed to have a plurality of blades, and the plurality of blades are evenly spaced along the circumference of the hub, and a channel for circulating liquid is defined between any two circumferentially adjacent blades, and a turbulent area is formed on the radial outer side of the suction surface of the blade; A vortex inducing structure is arranged on the suction surface of the blade and at the upstream boundary of the turbulent zone.

2. The double-suction centrifugal pump impeller according to claim 1, characterized in that: The boundary of the spoiler zone is inclined toward the radial inner side and close to the axial outer edge of the blade.

3. The double-suction centrifugal pump impeller according to claim 2, characterized in that: The dimensionless parameter of the blade flow direction at the upstream starting point of the boundary of the spoiler zone is S1, and satisfies 0.2≤S1≤0.4; the angle between the boundary of the spoiler zone and the flow direction is α, and satisfies 30°≤α≤60°.

4. The double-suction centrifugal pump impeller according to claim 3, characterized in that: The vortex-inducing structure is configured in plurality, and the plurality of vortex-inducing structures are arranged at intervals along the boundary of the spoiler area.

5. The double-suction centrifugal pump impeller according to claim 4, characterized in that: One of the plurality of vortex inducing structures is disposed at an upstream starting point of a boundary of the turbulence zone.

6. The double-suction centrifugal pump impeller according to claim 4, characterized in that: The vortex-inducing structure is a convex structure, and the equivalent diameter of the vortex-inducing structure is D, and satisfies 2mm≤D≤4mm.

7. The double-suction centrifugal pump impeller according to claim 6, characterized in that: The distance between two adjacent vortex-inducing structures is W, and satisfies 2D≤W≤4D.

8. The double-suction centrifugal pump impeller according to claim 7, characterized in that: The distances between two adjacent vortex-inducing structures are equal.

9. The double-suction centrifugal pump impeller according to claim 1, characterized in that: The vortex-inducing structure is integrally formed with the blade; or the vortex-inducing structure is connected to the blade by welding or bonding.

10. A method for preventing wear of a double-suction centrifugal pump impeller, characterized in that: A vortex inducing structure as described in any one of claims 1 to 9 is arranged on the suction surface of the blade.

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