Pumping impeller

Abstract

The pump impeller is used for driving cooling liquid and comprises a hollow outer cylinder, a hollow inner cylinder, a plurality of connecting ribs, a plurality of splitter blades and a magnet ring, the hollow outer cylinder is provided with an axis, an annular caulking groove and a penetrating groove, the annular caulking groove is formed in the outer surface of the hollow outer cylinder, and the penetrating groove penetrates through the hollow outer cylinder and is coaxial with the axis; the hollow outer cylinder is provided with a through groove, the hollow inner cylinder is arranged in the through groove, the hollow inner cylinder is provided with a shaft hole, the shaft hole penetrates through the hollow inner cylinder and is coaxial with the axis, the connecting ribs are connected between the hollow outer cylinder and the hollow inner cylinder, a flow channel is formed between any two adjacent connecting ribs, and the splitter blades are arranged at one end of the hollow outer cylinder. The splitter blades are arranged in a radial mode with the axis as the center, and the magnet ring is arranged in the annular caulking groove. Therefore, the pump impeller can be commonly used for an axial-flow pump and a centrifugal pump, and the effects of lightening and thinning, enhancing lubrication, dissipating heat and removing bubbles are achieved.

Description

Technical Field

[0001] This application relates to an impeller, and more particularly to a pump impeller applicable to both axial flow pumps and centrifugal pumps. Background Technology

[0002] With the rapid development of electronic technology, the performance of electronic components has gradually improved, and a large amount of heat is generated during operation. As a result, liquid cooling is widely used for heat dissipation of various electronic components due to its good heat dissipation efficiency. In order to improve the overall heat dissipation efficiency, liquid cooling often uses pumps to drive the flow of coolant, thereby increasing the flow rate and heat exchange rate of coolant to improve the cooling effect.

[0003] However, the required liquid cooling components and configurations vary depending on the type or form of electronic device, electronic equipment, or machine. Therefore, designers need to select axial or centrifugal pumps based on the application to meet different inlet and outlet liquid flow requirements. This results in impellers (rotors) being incompatible between different pumps. Furthermore, as electronic technology moves towards thinner and lighter designs, achieving a slimmer and lighter impeller, given the relatively large size and weight of traditional pump impellers, is another area that needs improvement.

[0004] In view of this, the applicant has devoted himself to researching and applying theoretical principles to address the shortcomings of the prior art, and has made every effort to solve the aforementioned problems, which has become the target of the applicant's improvement. Summary of the Invention

[0005] The main purpose of this application is to enable pump impellers to be used in both axial flow pumps and centrifugal pumps, and to achieve a thinner and lighter design.

[0006] To achieve the above objectives, this application provides a pump impeller for driving coolant and includes a hollow outer cylinder, a hollow inner cylinder, a plurality of connecting ribs, a plurality of flow-dividing blades, and a magnetic ring. The hollow outer cylinder has a centerline, an annular groove, and a through groove. The annular groove is disposed on the outer surface of the hollow outer cylinder, and the through groove penetrates the hollow outer cylinder and is coaxially arranged with the centerline. The hollow inner cylinder is disposed within the through groove and has a shaft hole that penetrates the hollow inner cylinder and is coaxially arranged with the centerline. Each connecting rib connects the hollow outer cylinder and the hollow inner cylinder. The adjacent connecting ribs, the inner wall of the hollow outer cylinder, and the outer wall of the hollow inner cylinder together form a flow channel. Each flow-dividing blade is set at one end of the hollow outer cylinder. The flow-dividing blades are arranged radially with the axis as the center. The magnetic ring is set in the annular groove. When the pump impeller rotates, the coolant is guided by each flow channel and divided into a first flow that enters the interior of the hollow outer cylinder and a second flow that flows on the outside of the hollow outer cylinder. The first flow flows outward after passing through the hollow inner cylinder along each flow channel, while the second flow flows outward under the influence of the rotation of each flow-dividing blade.

[0007] In one embodiment, each splitter blade includes a plurality of first splitter plates and a plurality of second splitter plates, each first splitter plate being arranged at equal angles, and each second splitter plate being arranged at equal angles and equally between any two adjacent first splitter plates.

[0008] In one embodiment, each first splitter plate is configured to correspond to each connecting rib, and each connecting rib is connected to the corresponding first splitter plate.

[0009] In one embodiment, a portion of the hollow inner cylinder protrudes from the hollow outer cylinder, and each first diverter plate is connected to the portion of the hollow inner cylinder that protrudes from the hollow outer cylinder.

[0010] In one embodiment, each second diverter plate has a guide ramp on the side facing the through slot.

[0011] In one embodiment, each guide ramp extends obliquely from the side of the corresponding second diverter plate facing the through slot toward the outer surface of the hollow outer cylinder and away from the hollow outer cylinder.

[0012] In one embodiment, the hollow outer cylinder has a plurality of demolding holes, each demolding hole being located on the side of the hollow outer cylinder where each flow divider blade is located.

[0013] In one embodiment, each flow divider blade has a plurality of demolding holes, each demolding hole being located on the side of each flow divider blade away from the hollow outer cylinder.

[0014] In one embodiment, a bearing is also included, which is disposed within the shaft hole.

[0015] In one embodiment, the magnet ring is a powerful magnet.

[0016] The pump impeller of this application has a hollow inner cylinder arranged in a slot in a hollow outer cylinder, and the hollow outer cylinder and the hollow inner cylinder are connected by connecting ribs to form multiple flow channels. Each flow divider blade is arranged at one end of the hollow outer cylinder. Therefore, the pump impeller of this application can be used in both axial flow pumps and centrifugal pumps, and achieves the effect of being lightweight and thin. Attached Figure Description

[0017] In the accompanying drawings, unless otherwise specified, the same reference numerals throughout the various drawings denote the same or similar parts or elements. These drawings are not necessarily drawn to scale. It should be understood that these drawings depict only some embodiments disclosed in this application and should not be construed as limiting the scope of this application.

[0018] Figure 1 This is a three-dimensional view of the present application.

[0019] Figure 2 This is a top view of this application.

[0020] Figure 3 This is a three-dimensional view of the appearance of this application from another perspective.

[0021] Figure 4 This is a cross-sectional side view of the application of this application to an axial flow pump.

[0022] Figure 5 This is a cross-sectional side view of the centrifugal pump applied in this application.

[0023] Figure 6 This is a top cross-sectional view of the centrifugal pump used in this application.

[0024] Explanation of reference numerals in the attached figures:

[0025] 10: Hollow outer cylinder;

[0026] 11: Centerline;

[0027] 12: Annular groove;

[0028] 13: Through groove;

[0029] 20: Hollow inner cylinder;

[0030] 21: Shaft hole;

[0031] 30: Connecting rib;

[0032] 31: Flow channel;

[0033] 40: Flow divider blades;

[0034] 41: First splitter plate;

[0035] 42: Second splitter plate;

[0036] 421: Guide ramp;

[0037] 50: Magnetic ring;

[0038] 60: Bearing;

[0039] 99: Demolding hole;

[0040] A: Axial flow pump;

[0041] A1, B1: body;

[0042] A11, B11: Chambers;

[0043] A13, B12: Liquid inlet;

[0044] A12, B13: Liquid outlet;

[0045] A2, B2: Stator;

[0046] B: Centrifugal pump;

[0047] L1: First branch;

[0048] L2: Second branch. Detailed Implementation

[0049] In the description of this application, it should be understood that the terms "front," "rear," "left," "right," "front end," "rear end," "end," "longitudinal," "lateral," "vertical," "top," and "bottom," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are used only for the convenience of describing this application and simplifying the description. They do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as limiting conditions of this application.

[0050] As used herein, terms such as "first," "second," "third," "fourth," and "fifth" describe various elements, components, regions, hierarchies, and / or parts, which should not be limited by these terms. These terms are used only to distinguish one element, component, region, hierarchy, or part from another. Unless the context clearly indicates otherwise, the use of terms such as "first," "second," "third," "fourth," and "fifth" herein does not imply order or sequence.

[0051] Unless otherwise defined, terms such as "substantially" and "approximately" are used to describe and narrate small changes. When used in the context of an event or situation, these terms may include the exact moment the event or situation occurred, or an approximate point in time. For example, when used in the context of a number, these terms may include a range of variation less than or equal to ±10% of the number, such as less than or equal to ±5%, less than or equal to ±4%, less than or equal to ±3%, less than or equal to ±2%, less than or equal to ±1%, less than or equal to ±0.5%, less than or equal to ±0.1%, or less than or equal to ±0.05%.

[0052] The detailed description and technical content of this application will be explained in conjunction with the accompanying drawings. However, the accompanying drawings are for illustrative purposes only and are not intended to limit the scope of this application.

[0053] This application provides a pump impeller applicable to either an axial flow pump A or a centrifugal pump B for driving coolant. Please refer to... Figures 1 to 3 As shown, the pump impeller of this application mainly includes a hollow outer cylinder 10, a hollow inner cylinder 20, a plurality of connecting ribs 30, a plurality of flow-dividing blades 40, and a magnet ring 50.

[0054] In this embodiment, the hollow outer cylinder 10 is a hollow cylindrical structure, but this application is not limited to this. Specifically, the hollow outer cylinder 10 has a centerline 11, an annular groove 12, and a through groove 13. The centerline 11 is the central axis of the hollow outer cylinder 10. The annular groove 12 is annular and is disposed on the outer surface of the hollow outer cylinder 10. The through groove 13 penetrates the hollow outer cylinder 10 to make the hollow outer cylinder 10 hollow, and the through groove 13 is a circular hole coaxially arranged with the centerline 11. In this embodiment, the annular groove 12 is an annular groove, and the annular groove 12 is located on one side of the hollow outer cylinder 10, but this application is not limited to this. For example, the annular groove 12 can also be a groove of other shapes, or the annular groove 12 can also be disposed in the middle section of the outer surface of the hollow outer cylinder 10.

[0055] The hollow inner cylinder 20 is positioned within the slot 13 of the hollow outer cylinder 10 at intervals (not labeled in the figure), and the centerlines 11 of the hollow inner cylinder 20 and the hollow outer cylinder 10 are coaxial. Specifically, the outer diameter of the hollow inner cylinder 20 is smaller than the diameter of the slot 13, thereby creating the interval between the inner wall of the hollow outer cylinder 10 and the outer wall of the hollow inner cylinder 20. The hollow inner cylinder 20 has a shaft hole 21. The shaft hole 21 penetrates the hollow inner cylinder 20, and the shaft hole 21 is also coaxial with the centerline 11.

[0056] Each connecting rib 30 connects the hollow outer cylinder 10 and the hollow inner cylinder 20. A flow channel 31 is formed between any two adjacent connecting ribs 30, the inner wall of the hollow outer cylinder 10, and the outer wall of the hollow inner cylinder 20 to allow coolant to pass through during pump impeller operation. That is, a plurality of flow channels 31 are formed between the hollow outer cylinder 10, the hollow inner cylinder 20, and each connecting rib 30. In this embodiment, the actual number of connecting ribs 30 is three, each connecting rib 30 is plate-shaped, and the connecting ribs 30 are substantially arranged at equal 120-degree angles to form three corresponding flow channels 31, thereby ensuring that the pump impeller of this application can rotate stably without tilting. However, this application is not limited to this, as long as the connecting ribs 30 are substantially arranged at equal angles.

[0057] Each diversion blade 40 is disposed at one end of the hollow outer cylinder 10. Specifically, in this embodiment, each diversion blade 40 is disposed on the end face of the hollow outer cylinder 10 away from the annular groove 12. Each diversion blade 40 is arranged radially with the axis 11 of the hollow outer cylinder 10 as the center, thereby ensuring that the pump impeller of this application can rotate stably without tilting.

[0058] A magnet ring 50 is disposed in the annular groove 12, corresponding to the pump stator on which the pump impeller of this application is installed. Specifically, in this embodiment, the magnet ring 50 is fixed to the annular groove 12 of the hollow outer cylinder 10 by plastic encapsulation injection molding. However, in other embodiments, the magnet ring 50 can also be fixed to the annular groove 12 of the hollow outer cylinder 10 by means of tight fitting, bonding, or welding. In this embodiment, the magnet ring 50 is a circular strong magnet, thereby reducing the thickness of the magnet ring 50 as much as possible under the required magnetic force to achieve a thinner profile. However, this application is not limited to this. In addition, since the magnet ring 50 and each diverter blade 40 are respectively disposed at opposite ends of the hollow outer cylinder 10, the weight of the pump impeller of this application can be balanced, thereby preventing one end from being too heavy and improving the stability of the pump impeller during rotation, making it less prone to skewing.

[0059] Therefore, since a hollow inner cylinder 20 is provided in the slot 13 of the hollow outer cylinder 10, and a plurality of flow channels 31 are formed between the hollow outer cylinder 10 and the hollow inner cylinder 20 by connecting ribs 30 to allow coolant to pass through, and a flow divider blade 40 is provided at one end of the hollow outer cylinder 10, the pump impeller of this application can be used in both axial flow pump A and centrifugal pump B, and achieves the effect of thinning.

[0060] Further explanation: In this embodiment, each diverter blade 40 includes a plurality of first diverter plates 41 and a plurality of second diverter plates 42. In this embodiment, the actual number of first diverter plates 41 and second diverter plates 42 is three each, but this application is not limited thereto. Each first diverter plate 41 and each second diverter plate 42 are substantially equally angularly arranged and staggered from each other, that is, arranged such that one second diverter plate 42 is arranged between two first diverter plates 41, thereby ensuring that the pump impeller of this application can rotate stably without tilting. In this embodiment, each first diverter plate 41 is respectively arranged corresponding to each connecting rib 30, and each connecting rib 30 is respectively connected to the bottom of the corresponding first diverter plate 41. That is, in this embodiment, the number of first diverter plates 41 is the same as the number of connecting ribs 30 and they are interconnected, thereby enhancing the overall structural strength of the pump impeller and improving the stability during rotation, but this application is not limited thereto. Each second diverter plate 42 is equally distributed between any two adjacent first diverter plates 41, thereby ensuring that the pump impeller of this application can rotate stably without tilting. In this embodiment, the number of first diverter plates 41 is the same as the number of second diverter plates 42, but in other embodiments, the number of first diverter plates 41 may be a multiple of the number of second diverter plates 42, or the number of second diverter plates 42 may be a multiple of the number of first diverter plates 41, as long as they can be symmetrically arranged.

[0061] Furthermore, in this embodiment, a portion of the hollow inner cylinder 20 protrudes beyond the hollow outer cylinder 10. Each first diverter plate 41 is connected to the portion of the hollow inner cylinder 20 that protrudes beyond the hollow outer cylinder 10; that is, each first diverter plate 41 extends radially from the portion of the hollow inner cylinder 20 that protrudes beyond the hollow outer cylinder 10 and connects to the end face of the hollow outer cylinder 10, thereby further strengthening the overall structural strength. In other words, the length of each first diverter plate 41 is slightly longer than the length of each second diverter plate 42. In addition, since each first diverter plate 41 is configured corresponding to each connecting rib 30, even if each first diverter plate 41 is connected to the portion of the hollow inner cylinder 20 that protrudes beyond the hollow outer cylinder 10, it will not affect the flow of coolant through each flow channel 31.

[0062] To further explain, each second diverter plate 42 has a guiding slope 421 formed on the side facing the through groove 13. Specifically, each guiding slope 421 extends obliquely from the side of the corresponding second diverter plate 42 facing the through groove 13 toward the outer surface of the hollow outer cylinder 10 and away from the hollow outer cylinder 10. In other words, each guiding slope 421 extends from the inner surface of the hollow outer cylinder 10 toward the outer surface of the hollow outer cylinder 10, and simultaneously extends from the end face of the hollow outer cylinder 10 away from that end face, thus presenting an oblique surface. Accordingly, when the pump impeller of this application rotates, the coolant can smoothly enter the flow channels 31 between the hollow outer cylinder 10, the hollow inner cylinder 20 and the connecting ribs 30, not only through the gap between each first diverter plate 41 and each second diverter plate 42, but also through the guidance of each guiding slope 421 of each second diverter plate 42. Specifically, when the pump impeller rotates, the coolant is guided by each flow channel 31 and divided into a first branch flow L1 that enters the interior of the hollow outer cylinder 10 and a second branch flow L2 that flows outside the hollow outer cylinder 10. The first branch flow L1 flows outward after passing through the hollow outer cylinder 10 along each flow channel 31, while the second branch flow L2 flows outward under the influence of the rotation of each branch blade 40.

[0063] It should be noted that, due to the small size and complex shape of the pump impeller of this application, its manufacturing process is not easy; and to ensure the overall structural strength, the pump impeller of this application, except for the magnet ring 50, is all injection molded from plastic. Therefore, the manufacturing process of the pump impeller of this application will be briefly described below so that those skilled in the art can implement it accordingly. First, in this embodiment, each first diverter plate 41 and the hollow inner cylinder 20 are integrally formed by the first plastic injection molding. Then, they and the magnet ring 50 are placed in the second molding mold for the second plastic injection molding to form the hollow outer cylinder 10, each second diverter plate 42 and each connecting rib 30, and the magnet ring 50 is tightly coupled to the annular groove 12 of the hollow outer cylinder 10. It should be understood that the foregoing process description is only intended to enable those skilled in the art to understand and is not intended to limit this application. Therefore, the pump impeller of this application is not limited to being manufactured using this process. Thus, any impeller with the same or similar structural improvements as the pump impeller of this application should still fall within the protection scope of this application. This is hereby stated.

[0064] Furthermore, in this embodiment, the hollow outer cylinder 10 and each flow divider blade 40 each have a plurality of demolding holes 99. However, this application is not limited to this; for example, only the hollow outer cylinder 10 may have a plurality of demolding holes 99, or only each flow divider blade 40 may have a plurality of demolding holes 99. Specifically, some of the demolding holes 99 are located on the side of the hollow outer cylinder 10 where each flow divider blade 40 is located, while the remaining demolding holes 99 are located on the side of each flow divider blade 40 away from the hollow outer cylinder 10. In this embodiment, each flow divider blade 40 with each demolding hole 99 is a first flow divider plate 41. However, in other embodiments, each second flow divider plate 42 may have each demolding hole 99, or both the first flow divider plate 41 and the second flow divider plate 42 may have each demolding hole 99. Therefore, through the arrangement of each ejection hole 99, the pump impeller of this application can be smoothly ejected after plastic injection molding, without the possibility of jamming and failure to eject due to its complex structure. More specifically, the ejection holes 99 provided on each of the first manifold plates 41 are used to eject each of the first manifold plates 41 and the hollow inner cylinder 20 together from the mold during the first plastic injection; while the ejection holes 99 provided on the hollow outer cylinder 10 are used to eject the entire impeller structure from the mold during the second plastic injection.

[0065] Further explanation: the pump impeller of this application also includes a bearing 60. The bearing 60 is disposed within the shaft hole 21. In this embodiment, the bearing 60 is made of ceramic material, thereby ensuring the wear resistance and thinness of the bearing 60, but this application is not limited thereto. Furthermore, in this embodiment, the bearing 60 is placed in the mold during the first plastic injection, so that the bearing 60 is tightly coupled to the shaft hole 21 of the hollow inner cylinder 20 during molding of each first diverter plate 41 and the hollow inner cylinder 20. However, in other embodiments, the bearing 60 can also be fixed within the shaft hole 21 of the hollow inner cylinder 20 by means of tight fitting, bonding, or welding. When the pump impeller is installed in... Figure 4 or Figure 5 When the pump's rotating shaft is driven to rotate, the coolant flows smoothly into the flow channels 31 between the hollow outer cylinder 10, the hollow inner cylinder 20, and the connecting ribs 30. This effectively lubricates and cools the bearing 60 and the rotating shaft assembly, extending the overall service life of the pump and improving its reliability. Furthermore, when air bubbles are present in the coolant, they are discharged through the flow channels 31 along with the coolant flow, preventing them from accumulating in the hollow outer cylinder 10, thus achieving a good venting effect.

[0066] Please continue reading. Figure 4 The diagram shows a schematic of the pump impeller of this application installed in an axial flow pump A. The axial flow pump A includes a body A1 and a stator A2. The body A1 has a chamber A11, an outlet A12, and an inlet A13. The outlet A12 and the inlet A13 are respectively located at opposite ends of the body A1, and the outlet A12 is connected to the inlet A13 via the chamber A11. The stator A2 is located adjacent to the inlet A13 and surrounds a portion of the chamber A11. The pump impeller of this application is located in the chamber A11, with the side provided with each flow divider blade 40 facing the outlet A12, and the side provided with the magnet ring 50 facing the inlet A13, thereby aligning the magnet ring 50 with the stator A2. Therefore, when the stator A2 is energized and generates magnetic force, it drives the magnet ring 50 to rotate the entire pump impeller, allowing the coolant to enter the flow channels 31 from the inlet A13 and exit from the outlet A12. Further, when the pump impeller rotates, the first branch flow L1 passes through the hollow outer cylinder 10 and is pushed into the outlet A12 by the branch flow blades 40. The second branch flow L2 flows along the gap between the magnet ring 50 and the surrounding chamber A11 and is pushed into the outlet A12 by the branch flow blades 40.

[0067] Please continue. Figures 5 to 6The diagram shows a schematic of the pump impeller of this application installed inside a centrifugal pump B. The centrifugal pump B includes a body B1 and a stator B2. The body B1 has a chamber B11, an inlet B12, and an outlet B13. The inlet B12 and outlet B13 are located on the side of the body B1, and the inlet B12 communicates with the outlet B13 via the chamber B11. The stator B2 is located on the body B1 and surrounds a portion of the chamber B11. The pump impeller of this application is located inside the chamber B11, and the side with each flow divider 40 faces the outlet B13, thereby aligning the magnet ring 50 with the stator B2. Thus, when the stator B2 is energized and generates magnetic force, it drives the magnet ring 50 to rotate the entire pump impeller. This allows the coolant to enter the chamber B11 through the inlet B12 for heat exchange, and then exit through the outlet B13 due to the centrifugal force generated by the rotation of the flow divider 40. To further explain, when the pump impeller rotates, the first stream L1 passes through the hollow outer cylinder 10 and flows along the gap between the magnetic ring 50 and the surrounding chamber B11. Driven by the respective stream vanes 40, it enters the outlet B13 and exits. The second stream L2 is also pushed out of the outlet B13 by the respective stream vanes 40. When the coolant contains air bubbles, they can be carried away from the pump impeller by the first stream L1 through the flow channels 31, preventing air bubbles from remaining in the hollow outer cylinder 10 and causing adverse effects on the pump impeller's operation.

[0068] The pump impeller of this application has a hollow inner cylinder 20 provided in the slot 13 of the hollow outer cylinder 10, and the hollow outer cylinder 10 and the hollow inner cylinder 20 are connected by connecting ribs 30 to form a plurality of flow channels 31. Each flow divider blade 40 is provided at one end of the hollow outer cylinder 10. Therefore, the pump impeller of this application can be used in both axial flow pump A and centrifugal pump B, and achieves the effect of being lightweight and thin.

[0069] In summary, the foregoing disclosure of this application is intended to enable those skilled in the art to clearly understand the technical content of this application and implement it accordingly, and is not intended to limit the scope of patent protection of this application. In addition, this application may of course have other embodiments not listed. Without departing from the spirit and substance of this application, those skilled in the art should be able to devise various corresponding changes and modifications based on this application, but all such corresponding changes and modifications should fall within the scope of protection of the patent claimed in this application.

Claims

1. A pump impeller for driving coolant, characterized in that, include: The hollow outer cylinder has a centerline, an annular groove and a through groove. The annular groove is disposed on the outer surface of the hollow outer cylinder, and the through groove penetrates the hollow outer cylinder and is coaxially arranged with the centerline. A hollow inner cylinder is disposed in the through groove. The hollow inner cylinder has a shaft hole that penetrates the hollow inner cylinder and is coaxial with the axis. A plurality of connecting ribs are connected between the hollow outer cylinder and the hollow inner cylinder, and a flow channel is formed between any two adjacent connecting ribs, the inner wall of the hollow outer cylinder, and the outer wall of the hollow inner cylinder. A plurality of flow divider blades are disposed at one end of the hollow outer cylinder, and each flow divider blade is arranged radially around the axis; and A magnet ring is disposed in the annular groove; When the pump impeller rotates, the coolant is divided into a first stream that enters the hollow outer cylinder and a second stream that flows outside the hollow outer cylinder, guided by the flow channels. The first stream flows outward after passing through the hollow inner cylinder along the flow channels, while the second stream flows outward under the influence of the rotation of the flow vanes.

2. The pump impeller according to claim 1, characterized in that, Each of the flow splitters includes a plurality of first flow splitters and a plurality of second flow splitters. Each of the first flow splitters is arranged at equal angles, and each of the second flow splitters is arranged at equal angles and in equal quantities between any two adjacent first flow splitters.

3. The pump impeller according to claim 2, characterized in that, Each of the first splitter plates is configured with a corresponding connecting rib, and each connecting rib is connected to the corresponding first splitter plate.

4. The pump impeller according to claim 2, characterized in that, A portion of the hollow inner cylinder protrudes from the hollow outer cylinder, and each of the first diverter plates is connected to the portion of the hollow inner cylinder that protrudes from the hollow outer cylinder.

5. The pump impeller according to claim 2, characterized in that, Each of the second diverter plates has a guide ramp formed on the side facing the through slot.

6. The pump impeller according to claim 5, characterized in that, Each of the guide ramps extends obliquely from the side of the corresponding second diverter plate facing the through slot toward the outer surface of the hollow outer cylinder and away from the hollow outer cylinder.

7. The pump impeller according to claim 1, characterized in that, The hollow outer cylinder has a plurality of demolding holes, each of which is located on the side of the hollow outer cylinder where the respective flow divider blade is located.

8. The pump impeller according to claim 1, characterized in that, Each of the flow divider blades has a plurality of demolding holes, and each demolding hole is located on the side of each flow divider blade away from the hollow outer cylinder.

9. The pump impeller according to claim 1, characterized in that, It also includes a bearing, which is disposed within the shaft bore.

10. The pump impeller according to claim 1, characterized in that, The magnetic ring is a powerful magnet.

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