Axial flux axial flow pump

Abstract

The invention provides an axial magnetic flux axial flow pump. The axial magnetic flux axial flow pump comprises a pump shell, a rotor and a supporting ring. A mounting hole is formed in the middle of the pump shell in the axial direction in a penetrating mode, an annular mounting cavity is formed in the inner circumferential wall of the mounting hole in a concave mode, the rotor comprises a cylinder part and a convex ring part, the cylinder part is rotationally connected to the upper portion of the mounting hole and axially limited in the mounting hole through a limiting structure, and the convex ring part is arranged in the annular mounting cavity. An annular cooling channel is formed between the outer wall of the convex ring part and the inner wall of the annular mounting cavity, a channel inlet is formed in the inner circumferential wall of the cylinder part, a cooling outlet of the annular cooling channel is formed in the bottom of the cylinder part in the circumferential direction, and a plurality of pressurizing blades are evenly distributed on the cylinder part in the circumferential direction. The pump body has the advantages that the rotor and the pressurizing blades are combined into a whole, a traditional pump shaft is omitted, the axial size is greatly shortened, extremely high power density is achieved, a heating core is directly scoured through the annular cooling channel, waste heat is directly and rapidly taken away by fluid, and the heat dissipation bottleneck is fundamentally solved.

Description

Technical Field

[0001] This invention relates to the field of axial flow pump technology, and more specifically, to an axial flux axial flow pump. Background Technology

[0002] Axial flux pumps have broad application prospects in industrial fluid transportation, new energy equipment and other fields due to their high power density and compact layout. However, the structural design defects of existing technologies limit their performance improvement and make it difficult to meet the stringent requirements of high-end scenarios.

[0003] Existing axial flux pumps generally suffer from low heat dissipation efficiency. A large amount of waste heat is generated when the motor stator windings are working, but due to the limited heat dissipation area at the stator windings, the heat is difficult to effectively dissipate. Traditional heat dissipation methods often rely on additional cooling devices, which not only increases structural complexity and axial dimensions, but also prevents the heat from being directly and quickly dissipated, creating a significant heat dissipation bottleneck. This severely limits the motor's power density, making it unable to operate stably under high load conditions for extended periods.

[0004] Meanwhile, traditional pump shaft-driven impellers present multiple drawbacks: To achieve impeller drive, traditional methods typically require a pump shaft that penetrates the flow channel, along with mechanical seals and connecting structures to ensure proper transmission between the rotor and impeller. The pump shaft not only interferes with the flow field and increases hydraulic losses, but its shaft seal also poses risks of leakage and wear, reducing system reliability and efficiency. Furthermore, the motor rotor and impeller are often connected separately, requiring high precision during assembly and presenting potential failure points such as loose key connections.

[0005] Therefore, developing an axial flux pump with high integration, excellent heat dissipation performance, compact structure and low flow resistance, and overcoming many limitations of existing technologies, has become a technical problem that urgently needs to be solved in this field. Summary of the Invention

[0006] This invention aims to overcome the shortcomings of the prior art and provide an axial flux pump with high integration, excellent heat dissipation performance, compact structure and low flow resistance. It achieves efficient and direct discharge of motor waste heat through an annular cooling channel. By combining the rotor and the booster blades into one, the traditional pump shaft is eliminated to reduce flow resistance and simplify the structure, thereby significantly improving the pump's power density, operating efficiency and long-term reliability.

[0007] To achieve the objectives of this invention, the following technical solutions are adopted: An axial flux axial flow pump includes a pump housing, a rotor, and a support ring. An axially penetrating mounting hole is provided in the middle of the pump housing. An annular mounting cavity is recessed circumferentially on the inner circumferential wall of the mounting hole. A first stator assembly and a second stator assembly are respectively provided in the pump housing on both axial sides of the annular mounting cavity. The rotor includes a cylindrical portion and a convex ring portion protruding circumferentially on the outer circumferential wall of the cylindrical portion. The cylindrical portion is rotatably connected to the mounting hole and axially limited within the mounting hole by a limiting structure. The convex ring portion is disposed within the annular mounting cavity and contains several circumferentially distributed permanent magnets. An annular cooling channel is formed between the outer wall of the convex ring portion and the inner wall of the annular mounting cavity. An inlet communicating with the cooling inlet of the annular cooling channel is provided on the inner circumferential wall of the cylindrical portion. The cooling outlet of the annular cooling channel is circumferentially located at the bottom of the cylindrical portion, and the cooling inlet is circumferentially connected to the mounting hole. Several pressure-boosting blades are evenly distributed circumferentially on the inner circumferential wall of the cylindrical portion. This pump body integrates the rotor and booster blades into one, eliminating the traditional pump shaft, significantly shortening the axial dimension, and achieving extremely high power density. It also innovatively utilizes the pumped fluid as a cooling medium, directly flushing the heat-generating core (convex ring, first stator assembly, second stator assembly and surrounding area) through a designed annular cooling channel, directly and quickly carrying away waste heat with the fluid. This fundamentally solves the heat dissipation bottleneck of axial flux motors, allowing them to operate continuously at higher power densities. At the same time, it eliminates the pump shaft and mechanical seal that penetrate the flow channel, eliminating shaft interference with the flow field and hydraulic losses caused by the shaft seal, thus improving pump efficiency.

[0008] Preferably, the annular cooling channel includes an inlet channel, an outlet channel, and a connecting channel connecting the inlet channel and the outlet channel. The inlet channel is disposed between the axial upper end face of the convex ring portion and the axial upper inner wall of the annular mounting cavity, and the inlet channel is radially distributed. The outlet channel is disposed between the axial lower end face of the convex ring portion and the axial lower inner wall of the annular mounting cavity, and the outlet channel is radially distributed. The connecting channel is disposed between the outer peripheral wall of the convex ring portion and the inner peripheral wall of the annular mounting cavity, and the connecting channel is axially distributed. The inlet of the inlet channel is connected to the inlet of the channel, the outlet of the inlet channel is connected to the axial upper end of the connecting channel, the axial lower end of the connecting channel is connected to the inlet of the outlet channel, and the outlet of the outlet channel is connected to the mounting hole. The radial-axial-radial combined loop formed by the aforementioned annular cooling channels ensures that the fluid flows orderly through the corresponding heat-generating areas of the stator assembly, achieving directional and full heat absorption. The cooling efficiency is significantly better than that of disordered flow channel designs. Furthermore, the radially distributed inlet and outlet channels, along with the axially distributed connecting channels, work together to ensure a smooth transition in fluid flow direction and velocity, avoiding the generation of local eddies and reducing interference with the main flow field. This balances cooling effect and hydraulic performance. At the same time, the annular flow channel structure ensures that the fluid evenly covers the area around the convex ring, allowing heat to be evenly dissipated on both sides of the stator assembly along the axial direction. This prevents component damage caused by local overheating and improves the operational stability of the equipment.

[0009] Preferably, there are multiple channel inlets, all of which are evenly distributed circumferentially and radially penetrate the inner circumferential wall of the cylindrical section. The flow rate of the cooling outlet is greater than the sum of the flow rates of all channel inlets. Multiple channel inlets allow fluid to be introduced simultaneously, significantly increasing the fluid flow rate and meeting the heat dissipation requirements of the stator assembly under high-power conditions. This avoids insufficient cooling caused by a single inlet. Furthermore, the circumferentially distributed channel inlets ensure that the cooling fluid enters the annular cooling channel uniformly, guaranteeing even heat dissipation from the stator assembly and preventing localized overheating that could affect motor performance and lifespan. The evenly distributed channel inlets also disperse the impact force during fluid introduction, reducing disturbance to the fluid flow in the main channel, minimizing additional hydraulic losses, and ensuring pump pressurization and delivery efficiency. The vertical flow difference ensures that some fluid flows through the annular cooling channel, carrying away heat and achieving better heat dissipation.

[0010] Preferably, any one of the aforementioned booster blades is positioned between two adjacent channel inlets, with the channel inlets located at the booster inlet at the upper axial end of the booster blade, and the booster outlet at the lower axial end of the booster blade extending to the lower port of the cylindrical portion. Furthermore, the angle between the blade outlet tangent and the radial horizontal plane is less than 90°. This interleaved arrangement of the booster blades avoids interference between the booster blades and the channel inlets, ensuring both efficient pressurization of the main body and smooth fluid flow into the annular cooling channel. This achieves synergistic optimization of boosting and cooling functions. The less than 90° angle of the booster blade outlet tangent conforms to fluid dynamics, reducing fluid separation and eddies at the blade outlet, minimizing local hydraulic losses, and avoiding obstruction of fluid flow into the annular cooling channel inlet, thus balancing boosting efficiency and cooling effect.

[0011] Preferably, the system also includes a support ring, which is fixedly connected to the lower axial part of the mounting hole, and the cylindrical part is rotatably connected to the upper axial part of the mounting hole. The support ring and the cylindrical part are axially spaced to form an annular flow gap communicating with the cooling outlet. A plurality of guide vanes are evenly distributed circumferentially on the inner peripheral wall of the support ring. The guide vanes within the support ring are used to rectify the fluid exiting the booster blades axially, preventing fluid loss and noise in the radial direction, thus facilitating the axial discharge of the fluid.

[0012] Preferably, the guide vane is integrally injection molded onto the support ring, and the vane outlet section is perpendicular to the radial horizontal plane. This integral molding eliminates the connection gap between the guide vane and the support ring, preventing vane loosening or deformation caused by fluid impact, improving the overall structural strength and fatigue resistance, adapting to high-load operation, simplifying the guide vane installation process, reducing assembly errors, and improving production efficiency. Simultaneously, the 90° outlet section design efficiently rectifies the fluid, recovers swirling kinetic energy, reduces fluid outlet loss and noise, and significantly improves the pump's hydraulic efficiency.

[0013] Preferably, the pump housing includes an upper housing and a lower housing. The upper housing has an axially extending upper through-hole in its center, and the first stator assembly is encased within the upper housing. The lower housing has an axially extending lower through-hole in its center, and the second stator assembly is encased within the lower housing. The upper and lower housings are detachably and fixedly connected together, with the upper and lower through-holes axially connected to form a mounting hole. An O-ring is also provided between the upper and lower housings to achieve a static seal. The detachable connection design of the pump housing facilitates rotor assembly, inspection, and maintenance, reducing disassembly difficulty and cost. Furthermore, the upper and lower housings respectively encapsulate the first and second stator assemblies, forming a modular structure design that facilitates standardized component production and mass manufacturing, improving production efficiency and product consistency. Simultaneously, the O-ring between the upper and lower housings provides a static seal, which, combined with the plastic encapsulation of the stator assembly, forms a double-seal protection, effectively isolating the external environment from the internal flow channel, preventing fluid leakage and the intrusion of external impurities, and improving the equipment's protection level.

[0014] Preferably, the limiting structure includes a bearing, a fixing cover, and a retaining ring; the inner peripheral wall of the axially upper part of the mounting hole is recessed along the circumferential direction with a first step, and the outer peripheral wall of the axially upper part of the cylindrical part is recessed along the circumferential direction with a second step; the outer peripheral wall of the bearing is circumferentially limited to the inner peripheral wall of the mounting hole, and the inner peripheral wall of the bearing is circumferentially limited to the outer peripheral wall of the cylindrical part, and the axial lower end of the bearing is limited on the first step and the second step; the fixing cover is fixedly connected to the axially upper end face of the pump housing, and the axial lower end face of the fixing cover abuts against the axially upper end face of the bearing; the retaining ring is disposed on the outer peripheral wall of the cylindrical part, and the axial lower end face of the retaining ring abuts against the axially upper end face of the bearing. The first step, the second step, the fixed cover, and the retaining ring work together to achieve dual circumferential and axial positioning of the bearing, ensuring the rotational positioning accuracy of the rotor's cylindrical part, reducing radial and axial movement during operation, improving the pump's operational stability, and ensuring that the bearing is subjected to uniform force, avoiding increased wear caused by localized stress concentration. The circumferential positioning of the bearing with the mounting hole and the cylindrical part prevents additional wear caused by relative sliding, extending the bearing's service life. At the same time, the various components of the positioning structure work together to form a stable support system, replacing the support function of the traditional pump shaft. This eliminates the need for the pump shaft while ensuring reliable rotation of the rotor assembly and reducing the risk of structural failure.

[0015] Preferably, a sealing structure is provided between the inner peripheral wall of the mounting hole and the outer peripheral wall of the cylindrical part, and the sealing structure is located axially above the bearing channel inlet; the sealing structure includes a sealing groove provided on the inner peripheral wall of the mounting hole and recessed along the circumference, and a sealing ring and a sealing ring installed in the sealing groove; the outer peripheral wall of the sealing ring seals and abuts against the inner peripheral wall of the sealing groove, the inner peripheral wall of the sealing ring seals and abuts against the outer peripheral wall of the sealing ring, and the inner peripheral wall of the sealing ring seals and abuts against the outer peripheral wall of the cylindrical part. By employing a combination of sealing rings and sealing collars, multiple sealing barriers are formed, effectively preventing fluid leakage from the flow channel to the bearing side, avoiding fluid erosion or contamination of the bearing, ensuring normal bearing operation, and the setting of the sealing groove allows the sealing structure to perfectly fit the pump housing and cylindrical part without interfering with the assembly and operation of other components; the tight fit between the sealing components ensures the sealing effect while not affecting the flexible rotation of the cylindrical part, ultimately preventing component corrosion and performance degradation caused by fluid leakage, reducing failures caused by seal failure, improving the overall reliability and service life of the pump body, and making it suitable for long-term operation under harsh working conditions.

[0016] Preferably, the permanent magnet and the booster blades are integrally injection molded onto the rotor. This method forms a robust whole, avoiding the risks of loosening and detachment associated with separate connections, improving the structural stability and impact resistance of the rotor assembly. Furthermore, the integral molding reduces the assembly steps for the permanent magnet and booster blades, lowering the accuracy requirements and assembly difficulty, and increasing production efficiency. It also avoids damage to components during assembly, ensuring consistent product quality. Additionally, the integral injection molding allows for complete sealing of the permanent magnet, preventing performance degradation caused by fluid erosion, extending the permanent magnet's lifespan, and ensuring stable motor drive efficiency.

[0017] The advantages of this invention are as follows: First, it offers a revolutionary improvement in heat dissipation performance. By encapsulating the stator assembly with a high thermal conductivity insulating material, and utilizing a dedicated annular cooling channel formed by the convex ring and the annular mounting cavity, the pumped fluid directly flows through the heat-generating area for efficient heat absorption, eliminating the need for additional cooling devices and completely resolving the heat dissipation bottleneck, thus supporting long-term stable operation of the motor under high power density. Second, it achieves extreme optimization in structural integration and compactness. The shaftless design eliminates shaft interference with the flow field and the risk of seal wear. The permanent magnet and booster blades, as well as the guide vanes and support ring, are integrally injection molded, reducing potential failure points from separate connections. The modular pump housing design further simplifies the structure and significantly reduces axial dimensions. Third, it significantly improves hydraulic efficiency. The optimized booster blade angle and the 90° outlet cross-section design of the guide vanes work synergistically to recover the kinetic energy of the fluid vortex, reducing hydraulic losses. The shaftless structure further reduces flow resistance. Fourth, the modular prefabrication and integrated molding process simplifies assembly, reduces alignment accuracy requirements, facilitates mass production and maintenance, and balances adaptability to harsh operating conditions with cost control. Attached Figure Description

[0018] Figure 1 is a structural schematic diagram of the axial flux axial flow pump of the present invention. Figure 2 is a perspective sectional view of the axial flux axial flow pump of the present invention. Figure 3 is a partial sectional view of the axial flux axial flow pump of the present invention. Figure 4 is an exploded schematic diagram of the axial flux axial flow pump of the present invention.

[0019] Explanation of reference numerals in the attached figures: 1. Pump housing; 11. Mounting hole; 111. First step; 112. Sealing groove; 12. Annular mounting cavity; 13. First stator assembly; 14. Second stator assembly; 101. Upper housing; 102. Lower housing; 103. O-ring; 2. Rotor; 21. Cylindrical part; 211. Channel inlet; 212. Second step; 22. Convex ring part; 221. Permanent magnet; 23. Pressure boosting blade; 231. Pressure boosting inlet; 232. Pressure boosting outlet; 23. Support ring; 30. Annular flow gap; 31. Guide vane; 4. Limiting structure; 41. Bearing; 42. Fixing cover; 43. Retaining ring; 5. Annular cooling channel; 501. Cooling inlet; 502. Cooling outlet; 51. Inlet channel; 52. Outlet channel; 53. Connecting channel; 6. Sealing structure; 61. Sealing ring; 62. Sealing ring. Detailed Implementation

[0020] First, those skilled in the art should understand that these embodiments are merely used to explain the technical principles of the embodiments of this application and are not intended to limit the scope of protection of the embodiments of this application. Those skilled in the art can make adjustments as needed to adapt to specific application scenarios.

[0021] In the description of the embodiments of this application, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this application based on the specific circumstances.

[0022] In the embodiments of this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0023] The present application will now be described in further detail with reference to the accompanying drawings and specific embodiments.

[0024] like Figures 1 to 4 As shown, an axial flux axial flow pump includes a pump housing 1, a rotor 2, and a support ring 3; the middle part of the pump housing 1 is axially ( Figure 1A mounting hole 11 is provided through the center (vertical direction). The mounting holes 11 are distributed circumferentially and radially on the inner peripheral wall of the axial center. Figure 1 The pump housing 1, located on the upper and lower sides of the annular mounting cavity 12, has a first stator assembly 13 and a second stator assembly 14 distributed circumferentially. The rotor 2 includes a cylindrical part 21 and a convex ring part 22 protruding circumferentially on the outer circumferential wall of the cylindrical part 21. In this embodiment, the convex ring part 22 is located in the lower axial part of the cylindrical part 21, and the cylindrical part 21 and the convex ring part 22 are coaxially arranged. The cylindrical part 21 is rotatably connected to the upper axial part of the mounting hole 11, and the cylindrical part 21 is axially limited in the mounting hole 11 by the limiting structure 4. The convex ring part 22 is installed in the annular mounting cavity 12. A plurality of permanent magnets 221 (magnetic tiles) are evenly distributed circumferentially in the convex ring part 22. The permanent magnets 221 are fixed by adhesive or insert injection molding and are arranged alternately to form a Halbach array or a conventional NS array, so that the permanent magnets 221 interact with the stator assemblies on the upper and lower sides. An annular cooling channel 5 is formed between the outer wall of the convex ring portion 22 and the inner wall of the annular mounting cavity 12. A channel inlet 211 communicating with the cooling inlet 501 of the annular cooling channel 5 is provided on the inner peripheral wall of the cylindrical portion 21. The cooling outlet 502 of the annular cooling channel 5 is arranged circumferentially at the bottom of the cylindrical portion 21, and the cooling inlet 501 is circumferentially connected with the mounting hole 11. Five spirally distributed pressurizing blades 23 are evenly distributed circumferentially on the inner peripheral wall of the cylindrical portion 21, and the five pressurizing blades 23 form a vortex. In this embodiment, the pressurizing blades 23 are airfoil-shaped blades, and the pressurizing blades 23 are inclined from the outside to the inside and from top to bottom. Since the fluid flowing out from the top is relatively turbulent and has axial and radial velocity components, the pressurization effect is further enhanced by the airfoil-shaped blades. The support ring 3 is fixedly connected to the lower axial part of the mounting hole 11 by connecting screws, and is spaced apart from the cylindrical part 21 to form an annular flow gap 30 communicating with the cooling outlet 502. The annular flow gap 30 is connected to the cooling outlet 502 and is slightly lower than the cooling outlet 502 to facilitate better downward flow of fluid into the support ring 3. Five spirally distributed guide vanes 31 are evenly distributed and fixedly connected to the inner circumferential wall of the support ring 3, forming a vortex shape. The guide vanes 31 are inclined from the outside to the inside and from the bottom to the top, and are arranged in the opposite direction to the booster vanes 23. In this embodiment, the guide vanes 31 are ordinary spiral vanes, used to rectify the fluid from the booster vanes 23 axially. The radial fluid will generate fluid loss and noise, thus facilitating the axial discharge of the fluid. Figure 2As shown, in this embodiment, the spiral centers of all guide vanes 31 are connected to the same support shaft, and the diameter of the support shaft gradually decreases from top to bottom and is coaxially arranged with the support ring 3. The support shaft further ensures the connection stability and connection strength of the guide vanes 31, and facilitates the stable axial rotation and discharge of fluid. The annular flow gap 30 allows the fluid to flow from the annular flow gap 30 to the support ring 3, and then be delivered out of the flow channel through the guide vanes 31. The pump body integrates the rotor 2 and the booster blades 23 into one, eliminating the traditional pump shaft, significantly shortening the axial dimension, and achieving extremely high power density. It also innovatively utilizes the pumped fluid as a cooling medium, directly flushing the heat-generating core (convex ring 22, first stator assembly 13, second stator assembly 14 and surrounding areas) through a designed annular cooling channel 5, directly and quickly carrying away waste heat with the fluid. This fundamentally solves the heat dissipation bottleneck of the axial flux motor, allowing it to operate continuously at higher power densities. Furthermore, the pump shaft and mechanical seal that penetrate the flow channel are eliminated, removing the shaft's interference with the flow field and the hydraulic losses caused by the shaft seal, thus improving pump efficiency.

[0025] like Figures 2 to 4 As shown, in this embodiment, the pump housing 1 includes an upper housing 101 and a lower housing 102. The upper housing 101 has an axially penetrating upper through-hole in its center, which is circular and gradually decreases in diameter from top to bottom in a stepped shape, facilitating the positioning and installation of the limiting structure 4. The first stator assembly 13 is enclosed within the upper housing 101. The lower housing 102 has an axially penetrating lower through-hole in its center, which is circular and gradually decreases in diameter from bottom to top in a stepped shape, facilitating the formation of the annular mounting cavity 12 and the positioning and installation of the support ring 3. The second stator assembly... Component 14 is encased within the lower housing 102. The upper housing 101 and lower housing 102 are detachably and fixedly connected together by connecting screws, and the upper and lower through holes are axially connected to form a mounting hole 11. The pump housing 1 adopts a detachable connection design, which facilitates the assembly, inspection, and maintenance of the rotor 2, reducing the difficulty and cost of disassembly and assembly. Furthermore, the upper housing 101 and lower housing 102 respectively encapsulate the first stator assembly 13 and the second stator assembly 14, forming a modular structure design, which facilitates standardized production and mass manufacturing of components, improving production efficiency and product consistency. In this embodiment, an O-ring 103 is also provided between the upper housing 101 and lower housing 102 to achieve static sealing between the two. Combined with the plastic encapsulation of the upper stator assembly, a double sealing protection is formed, effectively isolating the external environment from the internal flow channel, preventing fluid leakage and the intrusion of external impurities, and improving the equipment protection level.

[0026] like Figure 2 and Figure 3As shown, the annular cooling channel 5 (with annular cross-section) includes an inlet channel 51, an outlet channel 52, and a connecting channel 53 connecting the inlet channel 51 and the outlet channel 52. The inlet channel 51 is located between the axial upper end face of the convex ring portion 22 and the axial upper inner wall of the annular mounting cavity 12, and the inlet channel 51 is radially distributed. The outlet channel 52 is located between the axial lower end face of the convex ring portion 22 and the axial lower inner wall of the annular mounting cavity 12, and the outlet channel 52 is radially distributed. The connecting channel 53 is located between the outer peripheral wall of the convex ring portion 22 and the inner peripheral wall of the annular mounting cavity 12, and the connecting channel 53 is axially distributed. The inlet of the inlet channel 51 is connected to the channel inlet 211, the outlet of the inlet channel 51 is connected to the axial upper end of the connecting channel 53, the axial lower end of the connecting channel 53 is connected to the inlet of the outlet channel 52, and the outlet of the outlet channel 52 is connected to the mounting hole 11. The radial-axial-radial combined loop (flat annular flow channel gap) formed by the aforementioned annular cooling channel 5 ensures that the fluid flows orderly through the corresponding heat-generating area of ​​the stator assembly, achieving directional and full heat absorption. The cooling efficiency is significantly better than that of disordered flow channel design. Furthermore, the radially distributed inlet channel 51 and outlet channel 52, and the axially distributed connecting channel 53 work together to ensure a smooth transition in fluid flow direction and velocity, avoiding the generation of local eddies, reducing interference with the main flow field, and balancing cooling effect and hydraulic performance. At the same time, the annular flow channel structure ensures that the fluid evenly covers the area around the convex ring 22, allowing the heat to be evenly dissipated on both sides of the stator assembly, avoiding component damage caused by local overheating, and improving the operational stability of the equipment.

[0027] like Figures 1 to 2 As shown, in this embodiment, there are five channel inlets 211, and all channel inlets 211 are evenly distributed circumferentially and radially penetrate the inner circumferential wall of the cylindrical part 21. The flow rate of the cooling outlet 502 is greater than the sum of the flow rates of all channel inlets 211. During the pressurization process, the pressurizing blades 23 cause some fluid to enter the annular cooling channel 5 through the channel inlets 211. The flow difference between the upper and lower parts ensures that the fluid entering the annular cooling channel 5 can flow from top to bottom, and the fluid can flow out from the cooling outlet 502 below and flow back into the main fluid, thus carrying away the heat in the annular cooling channel 5. Fluid can be introduced simultaneously through multiple channel inlets 211, significantly increasing the fluid flow rate and meeting the heat dissipation requirements of the stator assembly under high-power conditions. This avoids the problem of insufficient cooling caused by a single inlet. Furthermore, the circumferentially distributed design of the channel inlets 211 ensures that the cooling fluid enters the annular cooling channel 5 evenly, ensuring that the heat of the stator assembly is evenly dissipated around the circumference, preventing local overheating from affecting the motor performance and service life. At the same time, the evenly distributed channel inlets 211 can disperse the impact force when the fluid is introduced, reducing disturbance to the fluid flow in the main channel, reducing additional hydraulic losses, and ensuring the pump body's pressurization and delivery efficiency.

[0028] Each booster blade 23 is positioned between two adjacent channel inlets 211. This interleaved placement of the booster blade 23 avoids interference between it and the channel inlets 211, ensuring both efficient pressurization of the main fluid by the booster blade 23 and smooth fluid flow into the annular cooling channel 5, thus achieving synergistic optimization of the boosting and cooling functions. The channel inlet 211 is located at the booster inlet 231 at the upper axial end of the booster blade 23, and the booster outlet 232 at the lower axial end of the booster blade 23 is located at the lower port of the cylindrical section 21. The placement of the booster blade 23 facilitates partial fluid entry into the annular cooling channel 5 and also facilitates better delivery of the pressurized fluid into the support ring 3. The angle between the blade outlet tangent of the booster blade 23 and the radial horizontal plane is less than 90°. The angle between the blade outlet section of the booster blade 23 and the radial horizontal plane is less than 90°. Through angle design, it conforms to the characteristics of fluid dynamics, which can reduce fluid separation and eddy currents at the blade outlet, reduce local hydraulic losses, and avoid obstructing the fluid introduction at the inlet of the annular cooling channel 5, thus balancing boosting efficiency and cooling effect.

[0029] like Figures 2 to 3 As shown, the limiting structure 4 includes a bearing 41, a fixing cover 42, and a retaining ring 43; the inner peripheral wall of the axially upward part of the mounting hole 11 (the upper through hole of the upper housing 101) is provided with a first step 111 recessed in the circumferential direction, and the cross section of the first step 111 is right-angled. The outer peripheral wall of the axially upward part of the cylindrical part 21 is provided with a second step 212 recessed in the circumferential direction, and the cross section of the second step 212 is right-angled, and it is arranged opposite to the first step 111. The outer peripheral wall of bearing 41 is circumferentially limited to the inner peripheral wall of mounting hole 11, and the inner peripheral wall of bearing 41 is circumferentially limited to the outer peripheral wall of cylindrical part 21. The inner and outer walls of the lower axial end of bearing 41 are limited on the first step 111 and the second step 212. The fixing cover 42 is fixedly connected to the upper axial end face of pump housing 1 by connecting screws, and the lower axial end face of fixing cover 42 abuts against the upper axial end face of bearing 41. The retaining ring 43 is clamped to the outer peripheral wall of cylindrical part 21 by snap ring, and the lower axial end face of retaining ring 43 abuts against the upper axial end face of bearing 41. The cooperation of the first step 111, the second step 212, the fixed cover 42, and the retaining ring 43 achieves dual circumferential and axial positioning of the bearing 41, ensuring the rotational positioning accuracy of the cylindrical part 21 of the rotor 2, reducing radial and axial movement during operation, improving the stability of the pump body, and ensuring that the bearing 41 is subjected to uniform force, avoiding increased wear caused by local stress concentration. The circumferential positioning cooperation between the bearing 41, the mounting hole 11, and the cylindrical part 21 prevents additional wear caused by relative sliding, extending the service life of the bearing 41. At the same time, the components of the positioning structure 4 work together to form a stable support system, replacing the support function of the traditional pump shaft, ensuring the reliable rotation of the rotor 2 module while eliminating the pump shaft, and reducing the risk of structural failure.

[0030] like Figure 3 and Figure 4 As shown, a sealing structure 6 is provided between the inner peripheral wall of the mounting hole 11 and the outer peripheral wall of the cylindrical portion 21. The sealing structure 6 is located axially above the bearing 41 channel inlet 211 and axially below the bearing 41, ensuring that fluid flowing in from the channel inlet 211 will not flow to the bearing 41. The sealing structure 6 includes a sealing groove 112 recessed circumferentially on the inner peripheral wall of the mounting hole 11, and a sealing ring 61 and a sealing ring 62 installed in the sealing groove 112. The sealing groove 112 facilitates the circumferential and radial limiting of the sealing ring 61 and the sealing ring 62. The outer peripheral wall of the sealing ring 62 seals and abuts against the inner peripheral wall of the sealing groove 112, the inner peripheral wall of the sealing ring 62 seals and abuts against the outer peripheral wall of the sealing ring 61, and the inner peripheral wall of the sealing ring 61 seals and abuts against the outer peripheral wall of the cylindrical portion 21. By combining sealing ring 61 and sealing ring 62, multiple sealing barriers are formed, effectively preventing fluid leakage from the flow channel to the bearing 41 side, avoiding fluid erosion or contamination of the bearing 41, ensuring the normal operation of the bearing 41, and the setting of sealing groove 112 makes the sealing structure 6 perfectly fit with the pump housing 1 and cylindrical part 21 without interfering with the assembly and operation of other components; the tight fit between the sealing elements ensures the sealing effect without affecting the flexible rotation of the cylindrical part 21, ultimately preventing component corrosion and performance degradation caused by fluid leakage, reducing failures caused by seal failure, improving the overall reliability and service life of the pump body, and making it suitable for long-term operation under harsh working conditions.

[0031] In this embodiment, the permanent magnet 221 and the booster blade 23 are integrally injection molded onto the rotor 2. This method forms a robust whole, avoiding the risks of loosening or detachment associated with separate connections, improving the structural stability and impact resistance of the rotor 2 module. Furthermore, the integral molding reduces the assembly steps between the permanent magnet 221 and the booster blade 23, lowering the accuracy requirements for alignment and assembly difficulty, thus improving production efficiency. It also avoids damage to components during assembly, ensuring consistent product quality. Additionally, the integral injection molding allows for complete sealing of the permanent magnet 221, preventing performance degradation caused by fluid erosion, extending the service life of the permanent magnet 221, and ensuring stable motor drive efficiency.

[0032] The guide vane 31 is integrally injection molded onto the support ring 3. The guide vane 31 is located at the upper port of the support ring 3, and the blade outlet cross-section of the guide vane 31 is perpendicular to the radial horizontal plane. The 90° design facilitates the axial discharge of fluid. The integral molding eliminates the connection gap between the guide vane 31 and the support ring 3, avoiding blade loosening or deformation caused by fluid impact, improving the overall structural strength and fatigue resistance, adapting to high-load operation, simplifying the installation process of the guide vane 31, reducing assembly errors, and improving production efficiency. At the same time, the 90° outlet cross-section design can efficiently rectify the fluid, recover swirling kinetic energy, reduce fluid outlet loss and noise, and significantly improve the hydraulic efficiency of the pump body.

[0033] like Figures 2 to 4 As shown, in this embodiment, both the first stator assembly 13 and the second stator assembly 14 are composed of a stator core, windings, and insulating components. The pump housing 1 is encapsulated with a high thermal conductivity insulating material (high thermal conductivity modified PPS or epoxy resin transfer molding), and the inner end face is a smooth plane. The high thermal conductivity insulating material encapsulation of the stator assembly can quickly conduct the heat generated by the stator core and windings. Combined with the design of the annular cooling channel 5, it can achieve efficient heat transfer to the fluid, solving the problem of slow heat dissipation of traditional stators. Furthermore, the seal formed by the encapsulation can achieve electrical insulation of the stator assembly, avoiding short circuit faults, and also isolate the fluid from the stator components, preventing corrosion and contamination, and improving the protection level. At the same time, the encapsulation process makes the stator assembly structure integrated, reducing additional insulating and sealing components, reducing the space occupied by the stator, and combined with the shaftless design, further improving the overall compactness of the pump body and meeting the installation requirements of narrow spaces.

[0034] In operation, the axial flux axial flow pump of this invention pumps fluid into the cylindrical section 21 through the axial inlet. After being pressurized by the booster blades 23, most of the fluid flows downward along the main flow channel, while a small portion enters the annular cooling channel 5 through the channel inlet 211. The fluid then flows sequentially through the inlet channel 51, the connecting channel 53, and the outlet channel 52, absorbing heat generated by the stator assembly during the flow. Subsequently, it merges into the main flow channel through the annular flow gap 30, and together with the main fluid, is rectified by the guide vanes 31 before being discharged from the axial outlet. Throughout the process, the cooling fluid directly contacts the stator assembly, achieving efficient heat dissipation. The shaftless design eliminates flow field interference and seal wear problems, and the integrated component structure improves equipment reliability and ease of assembly.

[0035] In summary, the advantages of this invention are: Revolutionary high-efficiency heat dissipation: By placing the heat-generating core (convex ring 22) in a specially designed annular cooling channel 5, fluid is forced into this annular cooling channel outside the main pumping path, directly flushing away and carrying away the heat generated by the permanent magnet 221 and the rotor 2. This design fundamentally solves the heat dissipation bottleneck of axial flux motors, achieving direct, active, and efficient cooling of the heat source, allowing the motor to operate continuously and stably at higher power and current densities.

[0036] Extremely compact and highly integrated: Employing an axial flux topology of "dual stator assembly clamping a single rotor 2," the pump itself has an extremely short axial dimension. Simultaneously, this invention integrates the motor rotor 2 and the pump impeller (booster blades) into a single rotor 2 module, completely eliminating the traditional long pump shaft. This shaftless design significantly shortens the overall pump's axial length, resulting in an exceptionally compact structure and a power density (power / volume or weight ratio) significantly higher than traditional shafted flux pumps or radial flux integrated pumps.

[0037] Low flow resistance and high hydraulic efficiency: By eliminating the pump shaft and mechanical seal, the interference of the shaft on the flow field, frictional losses at the shaft seal, and potential leakage paths are completely eliminated. The internal flow channel is smoother and more unobstructed, significantly reducing hydraulic losses. Combined with highly efficient rear guide vanes 31 to rectify the fluid, rotational kinetic energy is further recovered, thereby improving the overall hydraulic efficiency of the pump.

[0038] High reliability and long lifespan: The rotor module 2 (including permanent magnet 221 and booster blades 23) can be integrally injection molded to form a robust, sealed whole with strong corrosion resistance. The stator assembly is encapsulated with high thermal conductivity insulating material and forms a double seal with the split housing, providing a high level of protection. The shaftless design eliminates mechanical failure points such as key connection loosening and wear. The bearing 41 and sealing structure 6 are rationally designed to ensure long-term operational reliability.

[0039] Simplified process and assembly: The motor stator and housing can be prefabricated in modules, and the rotor is formed into a single integrated module. The assembly process mainly involves the alignment and connection between modules, which simplifies the complex processes required by traditional pumps, such as precision shaft alignment and shaft seal installation, thereby improving production efficiency and product consistency.

[0040] In the description of the embodiments of this application, it should be noted that the terms "inner" and "outer" and other terms indicating direction or positional relationship are based on the direction or positional relationship shown in the drawings. This is only for the convenience of description and does not indicate or imply that the device or component must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation of this application.

[0041] In the description of this application, the references to terms such as "an embodiment," "some embodiments," "in this embodiment," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in a suitable manner in any one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0042] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. An axial flux axial flow pump, characterized in that, The pump housing (1), rotor (2), and support ring (3) are included. A mounting hole (11) is axially provided in the middle of the pump housing (1). An annular mounting cavity (12) is recessed circumferentially on the inner circumferential wall of the mounting hole (11). A first stator assembly (13) and a second stator assembly (14) are respectively provided in the pump housing (1) on both axial sides of the annular mounting cavity (12). The rotor (2) includes a cylindrical part (21) and a convex ring part (22) circumferentially protruding from the outer circumferential wall of the cylindrical part (21). The cylindrical part (21) is rotatably connected to the mounting hole (11), and the cylindrical part (21) is axially limited within the mounting hole (11) by a limiting structure (4). The convex ring part (22) 22) Set in the annular mounting cavity (12), a number of permanent magnets (221) are evenly distributed in the circumferential direction in the convex ring (22). An annular cooling channel (5) is formed between the outer wall of the convex ring (22) and the inner wall of the annular mounting cavity (12). A channel inlet (211) is provided on the inner circumferential wall of the cylindrical part (21) and communicates with the cooling inlet (501) of the annular cooling channel (5). The cooling outlet (502) of the annular cooling channel (5) is arranged in the circumferential direction at the bottom of the cylindrical part (21) and the cooling inlet (501) is circumferentially connected to the mounting hole (11). A number of pressure boosting blades (23) are evenly distributed in the circumferential direction on the inner circumferential wall of the cylindrical part (21).

2. The axial flux pump according to claim 1, characterized in that, The annular cooling channel (5) includes an inlet channel (51), an outlet channel (52), and a connecting channel (53) connecting the inlet channel (51) and the outlet channel (52). The inlet channel (51) is located between the axial upper end face of the convex ring portion (22) and the axial upper inner wall of the annular mounting cavity (12), and the inlet channel (51) is radially distributed. The outlet channel (52) is located between the axial lower end face of the convex ring portion (22) and the axial lower inner wall of the annular mounting cavity (12), and the outlet channel is radially distributed. (52) is radially distributed. The connecting channel (53) is located between the outer peripheral wall of the convex ring (22) and the inner peripheral wall of the annular mounting cavity (12). The connecting channel (53) is axially distributed. The inlet of the inlet channel (51) is connected to the channel inlet (211). The outlet of the inlet channel (51) is connected to the upper axial end of the connecting channel (53). The lower axial end of the connecting channel (53) is connected to the inlet of the outlet channel (52). The outlet of the outlet channel (52) is connected to the mounting hole (11).

3. The axial flux pump according to claim 1, characterized in that, The number of channel inlets (211) is multiple, and all channel inlets (211) are evenly distributed circumferentially and radially penetrate the inner peripheral wall of the cylindrical part (21). The flow rate of the cooling outlet (502) is greater than the sum of the flow rates of all channel inlets (211).

4. The axial flux pump according to claim 3, characterized in that, Any of the aforementioned booster blades (23) is disposed between two adjacent channel inlets (211), and the channel inlets (211) are disposed at the booster inlet (231) at the upper axial end of the booster blade (23), the booster outlet (232) at the lower axial end of the booster blade (23) extends to the lower port of the cylindrical portion (21), and the angle between the blade outlet tangent of the booster blade (23) and the radial horizontal plane is less than 90°.

5. The axial flux pump according to claim 1, characterized in that, It also includes a support ring (3), which is fixedly connected to the lower axial part of the mounting hole (11), and the cylindrical part (21) is rotatably connected to the upper axial part of the mounting hole (11). The support ring (3) and the cylindrical part (21) are axially spaced to form an annular flow gap (30) communicating with the cooling outlet (502). Several guide vanes (31) are evenly distributed and fixedly connected on the inner circumferential wall of the support ring (3).

6. The axial flux pump according to claim 5, characterized in that, The guide vane (31) is integrally injection molded on the support ring (3), and the blade outlet section of the guide vane (31) is set perpendicular to the radial horizontal plane.

7. The axial flux pump according to claim 1, characterized in that, The pump housing (1) includes an upper housing (101) and a lower housing (102). The upper housing (101) has an axial through hole in the middle and the first stator assembly (13) is enclosed in the upper housing (101). The lower housing (102) has an axial through hole in the middle and the second stator assembly (14) is enclosed in the lower housing (102). The upper housing (101) and the lower housing (102) are detachably fixed together and the upper through hole and the lower through hole are axially connected to form a mounting hole (11). An O-ring (103) is also provided between the upper housing (101) and the lower housing (102) to achieve static sealing between them.

8. The axial flux pump according to claim 1 or 7, characterized in that, The limiting structure (4) includes a bearing (41), a fixing cover (42), and a retaining ring (43); the inner peripheral wall of the axially upward part of the mounting hole (11) is provided with a first step (111) in the circumferential direction, and the outer peripheral wall of the axially upward part of the cylindrical part (21) is provided with a second step (212) in the circumferential direction. The outer peripheral wall of the bearing (41) is circumferentially limited to the inner peripheral wall of the mounting hole (11), and the inner peripheral wall of the bearing (41) is circumferentially limited to the outer peripheral wall of the cylindrical part (21). The bearing (41) is positioned and its axial lower end is limited on the first step (111) and the second step (212). The fixed cover (42) is fixedly connected to the axial upper end face of the pump housing (1) and its axial lower end face abuts against the axial upper end face of the bearing (41). The retaining ring (43) is disposed on the outer peripheral wall of the cylindrical part (21) and its axial lower end face abuts against the axial upper end face of the bearing (41).

9. The axial flux pump according to claim 1, characterized in that, A sealing structure (6) is provided between the inner peripheral wall of the mounting hole (11) and the outer peripheral wall of the cylindrical part (21), and the sealing structure (6) is located axially above the inlet (211) of the bearing (41) channel; the sealing structure (6) includes a sealing groove (112) provided on the inner peripheral wall of the mounting hole (11) and recessed along the circumference, and a sealing ring (61) and a sealing ring (62) installed in the sealing groove (112); the outer peripheral wall of the sealing ring (62) is sealed and abutted against the inner peripheral wall of the sealing groove (112), the inner peripheral wall of the sealing ring (62) is sealed and abutted against the outer peripheral wall of the sealing ring (61), and the inner peripheral wall of the sealing ring (61) is sealed and abutted against the outer peripheral wall of the cylindrical part (21).

10. The axial flux pump according to claim 1, characterized in that, The permanent magnet (221) and the booster blade (23) are integrally injection molded onto the rotor (2).

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