Liquid pump

Abstract

This application discloses a liquid pump, including a stator, a rotor assembly located at the center of the stator, a pump fluid chamber for accommodating the impeller working on the axial end side of the rotor assembly, and multiple blades. A heat dissipation chamber for cooling the stator is formed on the radially outer side of the stator. A circumferentially extending through-slot is formed in the wall of the pump fluid chamber, which communicates with the heat dissipation chamber through the through-slot. Multiple blades are circumferentially spaced in the through-slot, and the length extension direction of each blade is parallel to the axial direction of the through-slot. This liquid pump achieves self-circulation of the liquid flow under pressure difference, improving heat dissipation efficiency. The multiple blades, circumferentially spaced in the through-slot with their length extension direction parallel to the axial direction of the through-slot, facilitate manufacturing, reduce fluid flow resistance, and further improve the heat dissipation efficiency by utilizing the centrifugal force generated by the multiple blades to accelerate and pressurize the fluid.

Description

Technical Field

[0001] This application relates to the field of liquid pump technology, and specifically to a liquid pump. Background Technology

[0002] Liquid pumps can be used in industrial server liquid cooling systems, refrigeration systems, etc. However, during the operation of liquid pumps, iron losses and copper losses are inevitable. These energy losses mainly manifest as heat. Copper losses are caused by the resistance of the copper coil in the motor part of the liquid pump. The resistance causes energy to be dissipated in the form of heat. Iron losses are caused by the hysteresis phenomenon and eddy current effect generated during the magnetization process of the iron core structure, which also causes electrical energy to be converted into heat energy. If this heat is not effectively dissipated, it will adversely affect the performance and service life of the liquid pump.

[0003] Liquid cooling technology effectively absorbs and transfers the heat generated during the operation of a liquid pump by circulating and cooling the liquid, ensuring that the liquid pump operates stably within its optimal temperature range.

[0004] In the process of developing this application, the inventors discovered at least the following technical problems in the prior art:

[0005] The existing heat dissipation structure of liquid pumps has several limitations and urgently needs to be improved to further enhance heat dissipation efficiency and system performance. Summary of the Invention

[0006] In order to effectively overcome the problems existing in the prior art, the main objective of this application is to provide a liquid pump that can improve heat dissipation efficiency.

[0007] To achieve the above objectives, this application specifically adopts the following technical solution:

[0008] A liquid pump includes a stator, a rotor assembly located at the center of the stator, a pumping chamber for accommodating the operation of an impeller on the axial end side of the rotor assembly, and a plurality of blades. A heat dissipation chamber for dissipating heat from the stator is formed on the radially outer side of the stator. A through groove extending circumferentially is formed in the wall of the pumping chamber, and the pumping chamber communicates with the heat dissipation chamber through the through groove.

[0009] The multiple blades are distributed circumferentially in the through groove, and the length extension direction of each blade is parallel to the axial direction of the through groove.

[0010] In some embodiments, the cross-section of the blade is arc-shaped along the radial direction of the through slot.

[0011] In some embodiments, the blade has a straight cross-section along the radial direction of the through slot.

[0012] In some embodiments, the blade has an airfoil-shaped cross-section along the radial direction of the through slot.

[0013] In some embodiments, the blade includes a first curved portion and a second curved portion connected to each other, the first curved portion being connected to the inner wall of one side of the through groove, the second curved portion being connected to the inner wall of the other side of the through groove, and the bending directions of the first curved portion and the second curved portion being opposite.

[0014] In some embodiments, the exit angle of the blade is an acute angle; or, the exit angle of the blade is a right angle; or, the exit angle of the blade is an obtuse angle.

[0015] In some embodiments, the plurality of blades are evenly distributed in the through slot at circumferential intervals.

[0016] In some embodiments, the radial dimension of the through slot gradually increases along the rotation direction of the rotor assembly.

[0017] In some embodiments, the liquid pump further includes a pump body and a shielding sleeve. The pump body has a stator cavity for accommodating the stator. The shielding sleeve is disposed at the center of the stator, and the shielding sleeve and the inner wall of the stator cavity enclose a rotor cavity. The rotor assembly is disposed within the rotor cavity.

[0018] In some embodiments, the liquid pump further includes a cylindrical shell, a first pump cover, and a second pump cover. A heat dissipation annular groove is formed on the radially outer side of the pump body. The cylindrical shell is fitted onto the pump body and seals the heat dissipation annular groove. The groove cavity of the heat dissipation annular groove is the heat dissipation cavity. The first pump cover is placed on one end of the pump body and surrounds the pump body to form the pump liquid cavity. The second pump cover is placed on the other end of the pump body and surrounds the pump body and the shielding sleeve to form the stator cavity and the rotor cavity.

[0019] Compared with the prior art, the liquid pump provided in this application has at least the following beneficial effects:

[0020] The pump fluid chamber of this application has a circumferentially extending through groove on its cavity wall. The pump fluid chamber is connected to the heat dissipation chamber through the through groove, and a high-pressure zone and a low-pressure zone can be formed within the pump fluid chamber. The liquid pressure in the high-pressure zone is greater than the liquid pressure in the low-pressure zone. Since the heat dissipation chamber can connect the high-pressure zone and the low-pressure zone of the pump fluid chamber through the through groove, when the liquid pump is working, under the action of pressure difference, the liquid in the pump fluid chamber can flow from the through groove into the heat dissipation chamber for heat exchange. After heat exchange, the liquid flows back from the heat dissipation chamber to the pump fluid chamber through the through groove, so that the liquid circulates repeatedly from high pressure to low pressure to remove the heat from the heat dissipation chamber, realizing the self-circulation of liquid flow. The circulation improves heat dissipation efficiency, reduces the need for an external power source, eliminates the need for additional piping structures, and helps reduce the size of the liquid pump. Furthermore, this application features multiple blades, which are circumferentially spaced in the through-slot. The length extension direction of each blade is parallel to the axial direction of the through-slot, simplifying manufacturing, reducing costs, and decreasing fluid flow resistance, thereby reducing energy loss. By utilizing the centrifugal force generated by the multiple blades to accelerate and pressurize the fluid, the heat dissipation efficiency of the liquid pump is further improved, thereby enhancing the overall performance of the system using this liquid pump. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the structure of a liquid pump provided in an embodiment of this application;

[0022] Figure 2 A cross-sectional view of a liquid pump provided in an embodiment of this application;

[0023] Figure 3 This is a schematic diagram of the pump body of the liquid pump provided in the embodiments of this application;

[0024] Figure 4 A schematic diagram of the pump body of the liquid pump provided in an embodiment of this application from another perspective;

[0025] Figure 5 This is a schematic diagram of the structure of the blades of a liquid pump provided in an embodiment of this application;

[0026] Figure 6 This is a schematic diagram of another embodiment of the blades of the liquid pump provided in this application.

[0027] Figure label:

[0028] 1. Stator; 2. Impeller; 3. Rotor assembly; 31. Rotor; 32. Shaft; 320. Protrusion; 4. Pump fluid chamber; 41. Through groove; 42. Flow channel; 5. Blade; 51. First end; 52. Second end; 53. First bend; 54. Second bend; 6. Heat dissipation chamber; 7. Pump body; 71. Liquid outlet; 72. Heat dissipation annular groove; 8. Shell; 9. First pump cover; 91. Liquid inlet; 10. Second pump cover; 11. Stator cavity; 110. Annular protrusion; 12. Rotor cavity; 13. Oil injector; 14. Cable connector; 15. First fin; 16. Second fin; 17. Limiter; 18. Mechanical shaft seal; 19. Sealing ring; 20. Shielding sleeve; 21. Stud; 22. Bearing; 23. Guide vane; 100. Liquid pump. Detailed Implementation

[0029] To make the objectives, technical solutions, and advantages of this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the scope of this application.

[0030] In the description of this application, unless otherwise expressly specified and limited, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance; unless otherwise specified or explained, the term "multiple" refers to two or more, and the term "various types" refers to two or more; the terms "connection," "fixed," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, an integral connection, or an electrical connection; it can be 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 this application according to the specific circumstances.

[0031] In the description of this specification, it should be understood that the directional terms such as "upper" and "lower" used in the embodiments of this application are used to describe the angles shown in the accompanying drawings and should not be construed as limiting the embodiments of this application. Furthermore, in the context, it should also be understood that when it is mentioned that an element is connected "upper" or "lower" to another element, it can be directly connected to the other element "upper" or "lower," or indirectly connected to the other element "upper" or "lower" through an intermediate element.

[0032] Liquid pumps typically employ liquid cooling for heat dissipation. Some liquid pumps feature a heat dissipation chamber on the radially outer side of the stator, allowing heat exchange with the stator. The inlet of this chamber is connected to the high-pressure zone of the pump's liquid chamber, while the outlet is connected via piping to the low-pressure zone. Heat dissipation is achieved through liquid circulation between the heat dissipation chamber and the pump's liquid chamber. However, this piping connection method is more expensive to manufacture and increases liquid flow resistance, thus reducing the pump's heat dissipation efficiency and resulting in relatively poor heat dissipation performance.

[0033] Therefore, this application provides a liquid pump to improve the above-mentioned problems.

[0034] Reference Figures 1-3 As shown, Figure 1 This is a schematic diagram of the structure of a liquid pump provided in an embodiment of this application. Figure 2 This is a cross-sectional view of a liquid pump provided in an embodiment of this application. Figure 3 This is a schematic diagram of the pump body of the liquid pump provided in this embodiment. This embodiment discloses a liquid pump 100, which includes a stator 1, a rotor assembly 3 located at the center of the stator 1, a pump liquid chamber 4 for accommodating the impeller 2 on the axial end side of the rotor assembly 3, and a plurality of blades 5. A heat dissipation chamber 6 is formed on the radially outer side of the stator 1 for dissipating heat from the outside of the stator 1, that is, the heat of the stator 1 can be transferred from the stator 1 to the cavity wall of the heat dissipation chamber 6 and then to the heat dissipation chamber 6. Since there is liquid in the heat dissipation chamber 6, the heat transferred to the heat dissipation chamber 6 will be absorbed by the liquid.

[0035] A circumferentially extending through groove 41 is formed on the edge of the pump fluid chamber 4. A high-pressure zone and a low-pressure zone can be formed within the pump fluid chamber 4. The liquid pressure in the high-pressure zone is greater than that in the low-pressure zone. The pump fluid chamber 4 is connected to the heat dissipation chamber 6 through the through groove 41; that is, the heat dissipation chamber 6 connects the high-pressure zone and the low-pressure zone of the pump fluid chamber 4 through the through groove 41. Multiple blades 5 are distributed circumferentially at intervals in the through groove 41, and the length extension direction of each blade 5 is parallel to the axial direction of the through groove 41. The axial direction is... Figure 2 The X direction and the radial direction are... Figure 2 The Y direction in the middle. It can be understood that the pump liquid chamber 4 has a liquid inlet (or inlet) and a liquid outlet (or outlet) to allow external liquid to flow into the pump liquid chamber 4 and to allow liquid to flow out of the pump liquid chamber 4, so as to realize liquid transportation.

[0036] It should be noted that the pressure difference between the high-pressure zone and the low-pressure zone is formed by the centrifugal force generated by the rotation of impeller 2. The principle of pressure difference refers to the difference in water pressure along the flow direction. When impeller 2 rotates, the rotational motion causes water flow. The area near the center line of impeller 2 is subject to low water pressure, while the area near the outer diameter of impeller 2 is affected by the water pressure of the high-pressure turbulent zone, resulting in a pressure difference. Furthermore, the interaction between impeller 2 and the inner wall of pump liquid chamber 4 generates a vortex effect, making the liquid flow in the entire pump liquid chamber 4 consistent with the characteristics of the centrifugal force of impeller 2 rotation. This allows the liquid to flow from the high-pressure zone to the low-pressure zone and flow into and out of the heat dissipation chamber 6, achieving reciprocating flow, and finally being discharged from the outlet. The specific positional relationship between the high-pressure zone and the low-pressure zone can be selected based on the actual structure of the impeller 2 and the pump liquid chamber 4. For example, in the pumping form of axial liquid inlet and radial liquid outlet, the area near the axis is the low-pressure zone, while the area away from the axis is the high-pressure zone. In the pumping form of radial liquid inlet and axial liquid outlet, the low-pressure zone and the high-pressure zone are opposite to the above. Generally speaking, the area near the liquid inlet is the low-pressure zone, while the area near the liquid outlet is the high-pressure zone.

[0037] It should be noted that the number of impellers 2 can be set according to the required flow rate of liquid cooling. It can be one layer of impellers 2 or multiple layers of impellers 2, which is not limited here.

[0038] In this embodiment, the liquid pump 100 also includes a guide vane 23, which is disposed at the outlet of the impeller 2 and is used to guide the flow of liquid. By combining the dynamic movement of the impeller 2 with the precise guidance of the guide vane 23, the energy efficiency of the liquid pump 100 is effectively maximized, thereby improving the efficiency of the liquid pump 100.

[0039] In this embodiment, the blade 5 and the inner wall of the through groove 41 are integrally formed to facilitate processing. It can be understood that in other embodiments, the blade 5 can also be detachably connected to the inner wall of the through groove 41, such as by threaded connection, snap-fit ​​connection, etc.

[0040] In this embodiment, there are eleven blades 5. The odd number of blades 5 can reduce the situation of symmetrical arrangement, thereby reducing the vibration and resonance when the liquid pump 100 rotates at high speed, reducing noise and its own vibration, improving the stability of blades 5, and facilitating dynamic balance correction. In specific applications, the number of blades 5 can be set as needed.

[0041] In this embodiment, the pump fluid chamber 4 has a circumferentially extending through groove 41 on its cavity wall. The pump fluid chamber 4 is connected to the heat dissipation chamber 6 through the through groove 41. A high-pressure zone and a low-pressure zone can be formed within the pump fluid chamber 4, with the liquid pressure in the high-pressure zone being greater than that in the low-pressure zone. Since the heat dissipation chamber 6 can connect the high-pressure zone and the low-pressure zone of the pump fluid chamber 4 through the through groove 41, when the liquid pump is working, under the action of the pressure difference, the liquid in the pump fluid chamber 4 can flow from the through groove 41 into the heat dissipation chamber 6 for heat exchange. After heat exchange, the liquid flows back from the heat dissipation chamber 6 to the pump fluid chamber 4 through the through groove 41, causing the liquid to circulate repeatedly from high pressure to low pressure, thereby carrying away the heat from the heat dissipation chamber 6 and achieving… The self-circulating liquid flow improves heat dissipation efficiency, reduces the need for an external power source, eliminates the need for additional piping structures, and helps reduce the size of the liquid pump 100. Furthermore, this application also includes multiple blades 5, which are distributed circumferentially in the through groove 41. The length extension direction of each blade 5 is parallel to the axial direction of the through groove, making manufacturing simpler, reducing costs, and decreasing fluid flow resistance, thereby reducing energy loss. Moreover, by utilizing the centrifugal force generated by the multiple blades 5 to accelerate and pressurize the fluid, the heat dissipation efficiency of the liquid pump 100 is further improved, thereby enhancing the overall performance of the system using this liquid pump 100.

[0042] Reference Figure 3 and Figure 4 As shown, Figure 4 This is a schematic diagram of the pump body of the liquid pump provided in this embodiment of the application from another perspective. The radial dimension of the through groove 41 gradually increases along the rotation direction of the rotor assembly 3 (i.e., the forward rotation direction of the liquid pump 100), which promotes the formation of vortices, increases the flow rate of the liquid, and enables more uniform liquid circulation and heat distribution in the heat dissipation cavity 6, thereby improving the heat dissipation efficiency of the liquid pump 100. Furthermore, the length of the through groove 41 extends along the Archimedean spiral, so as to guide, accelerate, and pressurize the fluid by utilizing the characteristics of the Archimedean spiral, thereby further improving the heat dissipation efficiency of the liquid pump 100.

[0043] In this embodiment, the inner wall of the pump liquid chamber 4 is formed with a flow channel 42 extending along the Archimedean spiral. The flow channel 42 is located between the inner wall of the pump liquid chamber 4 and the through groove 41 in the radial direction. One end of each blade 5 is connected to the inner wall of the through groove 41, and the other end of each blade 5 is connected to the flow channel 42. The axial direction of the flow channel 42 is consistent with the axial direction of the impeller 2. By utilizing the characteristics of the Archimedean spiral, the fluid is guided, accelerated, and pressurized, converting the kinetic energy of the liquid at the outlet of the impeller 2 into pressure energy, so that the liquid is accelerated to flow into and out of the heat dissipation chamber 6, further improving the heat dissipation efficiency of the liquid pump 100.

[0044] In this embodiment, multiple blades 5 are evenly distributed in the through groove 41 at circumferential intervals, so that the pressure and flow rate borne by each blade 5 are uniform during operation, reducing energy loss caused by pressure fluctuations and extending the service life of the liquid pump 100. It can be understood that in other embodiments, the multiple blades 5 can also be unequally spaced blades. The multiple blades 5 are set along the flow channel 42 of the Archimedean spiral from the starting point to the end point. The pressure fluctuations are progressively increased with the multiple blades 5 at unequal distances, the pressure difference of the impeller 2 is enhanced, the eddy current of "stirring" is enhanced, the boundary layer of the pump liquid chamber 4 and the heat dissipation chamber 6 is broken, thereby accelerating heat exchange and improving heat exchange efficiency.

[0045] Reference Figure 3 and Figure 5 As shown, Figure 5 This is a schematic diagram of the structure of the blade of the liquid pump provided in this application embodiment. Along the radial direction of the through groove 41, the cross-section of the blade 5 is arc-shaped. The arc-shaped blade 5 design enables the liquid to exhibit a scanning flow when passing through it, which can increase the liquid flow rate and improve the flow rate of the liquid pump 100. Furthermore, its streamlined design makes the liquid flow more uniform, reduces the friction between the liquid and the surface of the blade 5, thereby extending the service life of the liquid pump 100. It also reduces the flow resistance of the liquid and increases the operating efficiency of the liquid pump 100.

[0046] In this embodiment, the outlet angle α of blade 5 is an acute angle, i.e., a backward-curved blade. The backward-curved blade makes the flow path of the fluid when passing through blade 5 more in line with the curve of blade 5, reducing fluid stall and leakage, thereby reducing the energy loss of liquid pump 100. The flow channel of the backward-curved blade is shorter and the flow velocity is higher, which is suitable for high flow rate conditions. In the radial direction of the through groove 41, blade 5 has a first end 51 and a second end 52. The distance of the second end 52 from the axis of the pump is greater than the distance of the first end 51 from the axis of the pump. The outlet angle α of blade 5 is the angle between the tangent at the second end 52 in the axial direction and the straight extension line of blade 5 at the second end 52. In specific applications, the outlet angle α of blade 5 can also be a right angle, i.e., a radial blade. Radial blades convert more effective energy, have less hydraulic loss, and are more efficient. Radial blades are suitable for efficient and stable conditions. Alternatively, the outlet angle α of blade 5 can also be an obtuse angle, i.e., a forward-curved blade. This design can increase the head of liquid pump 100 and is suitable for low flow rate and high head conditions.

[0047] In some embodiments, the cross-section of the blade 5 is straight along the radial direction of the through groove 41. The straight blade 5 has a simple structure, low manufacturing cost, and wide applicability. The straight blade 5 makes the fluid flow on the blade 5 more stable and the flow resistance is relatively small, thereby improving the heat dissipation efficiency of the liquid pump 100.

[0048] In some embodiments, along the radial direction of the through groove 41, the cross section of the blade 5 is airfoil-shaped. The airfoil-shaped blade 5 is designed similarly to the airfoil of an airplane, forming a certain curvature on the cross section and creating a difference between the upper and lower surfaces. This design can generate lift in the fluid, thereby increasing the water flow velocity and pressure, thus improving the efficiency and stability of the liquid pump 100.

[0049] Reference Figure 6 As shown, Figure 6 This is a schematic diagram of another embodiment of the blade of the liquid pump provided in this application. In some embodiments, the blade 5 includes a first curved portion 53 and a second curved portion 54 connected to each other. The first curved portion 53 is connected to the inner wall on one side of the through groove 41, and the second curved portion 54 is connected to the inner wall on the other side of the through groove 41. The bending directions of the first curved portion 53 and the second curved portion 54 are opposite. By combining the characteristics of a forward-curved blade and a backward-curved blade, the liquid pump 100 can maintain high efficiency and performance under different operating conditions, thereby improving the efficiency of the liquid pump 100.

[0050] Reference Figure 1 and Figure 2 As shown, the liquid pump 100 includes a pump body 7, a cylindrical shell 8, a first pump cover 9, a second pump cover 10, and a shielding sleeve 20. The pump body 7 has a liquid outlet 71 communicating with the pump liquid chamber 4, and a heat dissipation annular groove 72 is formed on the radially outer side of the pump body 7. The cylindrical shell 8 is fitted onto the pump body 7 and seals the heat dissipation annular groove 72, the groove cavity of which is a heat dissipation chamber 6. The first pump cover 9 is connected to the pump body 7 by studs 21 and covers one end of the pump body 7, forming the pump liquid chamber 4 with the pump body 7, and an inlet 91 communicating with the pump liquid chamber 4 is formed in the axial center of the first pump cover 9. The second pump cover 10 is connected to the pump body 7 by studs 21 and covers the other end of the pump body 7, forming the stator cavity 11 with the pump body 7. The stator cavity 11 has an annular protrusion 110 on its cavity wall. The shielding sleeve 20 is fitted onto the annular protrusion 110 and located at the center of the stator 1, so that the shielding sleeve 20, the inner wall of the stator cavity 11, and the second pump cover 10 enclose the rotor cavity 12. The rotor assembly 3 is disposed in the rotor cavity 12. The shielding sleeve 20 effectively ensures the sealing of the rotor assembly 3, thereby reducing the contact between the coolant and the rotor assembly 3 and the resulting corrosion of the rotor assembly 3. This effectively ensures the normal operation of the rotor assembly 3 and extends the service life of the rotor assembly 3. In addition, the shielding sleeve 20 can absorb the heat generated by the rotor assembly 3 during operation and transfer the heat to the coolant through its material, thereby playing a role in heat dissipation.

[0051] In this embodiment, the inlet 91 is located at the radial center of the impeller 2, and the outlet 71 is located at the radial outer end of the impeller 2, so that the fluid is output radially outward. The radial output flow rate is large and can withstand high pressure. It can be understood that in other embodiments, it can also be a pumping form with an axial inlet 91 and an axial outlet 71; or a pumping form with a radial inlet 91 and a radial outlet 71; or a pumping form with a radial inlet 91 and an axial outlet 71.

[0052] In this embodiment, the heat dissipation cavity 6 is an annular cavity surrounding the stator 1, so as to effectively ensure that there is a larger heat exchange area between the heat dissipation cavity 6 and the stator 1, thereby improving the heat dissipation efficiency. It can be understood that in other embodiments, the heat dissipation cavity 6 may also be a strip cavity extending along the axial direction. Specifically, there may be only one strip cavity or multiple strip cavities arranged in parallel circumferentially.

[0053] In this embodiment, the pump body 7 is also provided with an oil inlet 13 and a cable connector 14. The oil inlet 13 and the cable connector 14 are respectively connected to the stator cavity 11. Immersion coolant (insulating coolant) is injected through the oil inlet 13. The coolant absorbs the heat generated during the operation of the stator 1 and rotor assembly 3, and then conducts it to the heat dissipation cavity 6. The liquid in the heat dissipation cavity 6 carries away the heat, thereby maintaining the temperature of the stator 1 and rotor assembly 3 within a safe operating range. The cable connector 14 is used for cable insertion to energize the stator 1 and transmit external control signals to the stator 1 inside the pump body 7. This allows the control components to be located on the outside of the pump body 7 for convenient heat dissipation and maintenance.

[0054] Continue to refer to Figure 2 As shown, the rotor assembly 3 includes a rotor 31 and a shaft 32, with the rotor 31 housed within the rotor cavity 12. The shaft 32 is rotatably connected to the pump body 7 via a bearing 22, which reduces friction between the shaft 32 and the pump body 7 to ensure smooth operation of the shaft 32. One end of the shaft 32 passes through the rotor 31, and the other end passes through the pump liquid cavity 4 and is connected to the impeller 2 within the pump liquid cavity 4. The shaft 32 has a protrusion 320. The liquid pump 100 also includes a limiter 17, which is fitted onto the shaft 32 and located within the rotor cavity 12. One end of the rotor 31 abuts against the protrusion 320, and the other end of the rotor 31 abuts against the limiter 17. The protrusion 320 and the limiter 17 limit the rotor 31 axially, reducing axial displacement of the rotor 31 during rotation and effectively ensuring stable operation of the liquid pump 100. Understandably, the rotor cavity 12 is filled with refrigerant oil, which serves two purposes: firstly, to ensure the lubrication of the rotor assembly 3, and secondly, to transfer heat to the shielding sleeve 20 through the refrigerant oil.

[0055] In this embodiment, the liquid pump 100 also includes a mechanical shaft seal 18, which is sleeved on the rotating shaft 32 and abuts against the pump body 7 to ensure the sealing between the rotating shaft 32 and the pump body 7 when the rotating shaft 32 passes through the pump body 7, thereby ensuring the sealing between the pump liquid chamber 4 and the rotor chamber 12.

[0056] Reference Figure 2 As shown, the liquid pump 100 also includes multiple sealing rings 19. The first pump cover 9 has a circumferentially extending groove, and the sealing ring 19 is disposed in the groove and abuts against the inner wall of the pump body 7 to ensure the sealing of the connection between the first pump cover 9 and the pump body 7. The outer wall surface of the annular protrusion 110 has a groove, and the sealing ring 19 is disposed in the groove and abuts against the inner wall of the shielding sleeve 20 to ensure the sealing of the connection between the shielding sleeve 20 and the annular protrusion 110. The second pump cover 10 has a circumferentially extending groove, and the sealing ring 19 is disposed in the groove and abuts against the inner wall of the pump body 7 to ensure the sealing of the connection between the second pump cover 10 and the pump body 7. Furthermore, the second pump cover 10 has a boss corresponding to the annular protrusion 110, and the outer wall surface of the boss has a groove, and the sealing ring 19 is disposed in the groove and abuts against the inner wall of the shielding sleeve 20 to ensure the sealing of the rotor cavity 12.

[0057] Reference Figure 3 As shown, the bottom wall of the heat dissipation annular groove 72 is provided with multiple first fins 15 spaced apart. The bottom wall of the heat dissipation annular groove 72 is the wall surface of the heat dissipation annular groove 72 in the radial direction near the stator 1. The inner wall surface of the stator cavity 11 is provided with multiple second fins 16 spaced apart, so as to increase the heat exchange area by means of the first fins 15 and the second fins 16. In this way, the heat dissipation efficiency is improved by utilizing the synergistic effect of the fin heat dissipation structure and liquid cooling. The fins can also play a role in turbulence, thereby improving the heat exchange capacity and improving the heat dissipation efficiency. The multiple first fins 15 and the multiple second fins 16 can be arranged at equal intervals or at unequal intervals.

[0058] In this embodiment, the heights of the multiple first fins 15 are different. Fins of unequal height can guide fluid flow more effectively, thereby increasing the contact area and time between the fluid and the fin surface and improving heat exchange efficiency. It is understood that in other embodiments, the heights of the multiple first fins 15 may also be the same.

[0059] In this embodiment, each first fin 15 is inclined, that is, the angle between the first fin 15 and the bottom wall of the pump liquid chamber 4 is not equal to 90°, so that the multiple first fins 15 are arranged in a spiral shape. The spiral shape is intended to enhance the vortex motion of the fluid, promote turbulence, thereby further breaking the boundary layer and increasing the heat transfer coefficient. Moreover, the spiral fins can provide more surface area in a limited space and guide the fluid to move along a specific path, thereby achieving more efficient heat exchange in a smaller space and further improving heat dissipation efficiency. It can be understood that in other embodiments, the angle between the first fin 15 and the bottom wall of the pump liquid chamber 4 can also be equal to 90°.

[0060] The liquid pump 100 also includes a fan impeller and a guide shroud. The guide shroud is located on the side of the second pump cover 10 facing away from the pump body 7, and the guide shroud and the second pump cover 10 enclose a space for the fan impeller to work. One end of the rotating shaft 32 passes through the second pump cover 10 and extends into the space. The fan impeller is sleeved on the rotating shaft 32 and located in the space. When the rotating shaft 32 rotates, it can drive the fan impeller to rotate together, thereby dissipating the heat generated by the stator 1 and the rotor 31 during operation, and further improving the heat dissipation efficiency.

[0061] The outer surface of the shell 8 is provided with multiple third fins that are spaced apart along the circumference of the shell 8, and the second pump cover 10 is provided with multiple fourth fins on the side facing away from the pump body 7, so as to further increase the heat exchange area and thus further improve the heat exchange efficiency.

[0062] In specific application scenarios, during operation, the inlet 91 of the liquid pump 100 is connected to a water source (fluid source), and the cable is connected to the stator 1 through the cable connector 14, converting electrical energy into mechanical energy. The stator 1 drives the rotor 31 and the shaft 32 to rotate, thereby driving the impeller 2 to rotate. The centrifugal force of the rotating impeller 2 generates a vortex effect, drawing water into the pump liquid chamber 4 through the inlet 91. Under the action of pressure difference, a portion of the water in the pump liquid chamber 4 flows into and out of the heat dissipation chamber 6 through the through groove 41 for circulation and heat dissipation, realizing self-circulation of the liquid flow. The heat extracted from the heat dissipation chamber 6 can be extracted from the outlet 71 of the pump liquid chamber 4, thereby achieving continuous heat dissipation and meeting the requirements of high heat dissipation rate.

[0063] The above description is merely a preferred 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. A liquid pump characterized by, It includes a stator, a rotor assembly located at the center of the stator, a pump chamber for accommodating the impeller working on the axial end side of the rotor assembly, and multiple blades. A heat dissipation cavity for dissipating heat from the stator is formed on the radially outer side of the stator. A through groove extending circumferentially is opened in the cavity wall of the pump chamber, and the pump chamber communicates with the heat dissipation cavity through the through groove. The multiple blades are distributed circumferentially in the through groove, and the length extension direction of each blade is parallel to the axial direction of the through groove.

2. The liquid pump of claim 1, wherein, Along the radial direction of the through groove, the cross-section of the blade is arc-shaped.

3. The liquid pump of claim 1, wherein, Along the radial direction of the through groove, the cross-section of the blade is linear.

4. The liquid pump according to claim 1, characterized in that, Along the radial direction of the through groove, the cross-section of the blade is airfoil-shaped.

5. The liquid pump according to claim 1, characterized in that, The blade includes a first curved portion and a second curved portion that are connected to each other. The first curved portion is connected to the inner wall of one side of the through groove, and the second curved portion is connected to the inner wall of the other side of the through groove. The bending directions of the first curved portion and the second curved portion are opposite.

6. The liquid pump according to claim 1, characterized in that, The exit angle of the blade is an acute angle; or, the exit angle of the blade is a right angle; or, the exit angle of the blade is an obtuse angle.

7. The liquid pump according to claim 1, characterized in that, The multiple blades are evenly distributed in the through slot at circumferential intervals.

8. The liquid pump according to claim 1, characterized in that, The radial dimension of the through slot gradually increases along the rotation direction of the rotor assembly.

9. The liquid pump according to any one of claims 1 to 8, characterized in that, The liquid pump also includes a pump body and a shielding sleeve. The pump body has a stator cavity for accommodating the stator. The shielding sleeve is disposed at the center of the stator, and the shielding sleeve and the inner wall of the stator cavity enclose a rotor cavity. The rotor assembly is disposed in the rotor cavity.

10. The liquid pump according to claim 9, characterized in that, The liquid pump also includes a cylindrical shell, a first pump cover, and a second pump cover. A heat dissipation annular groove is formed on the radial outer side of the pump body. The cylindrical shell is fitted onto the pump body and seals the heat dissipation annular groove. The groove cavity of the heat dissipation annular groove is the heat dissipation cavity. The first pump cover is placed on one end of the pump body and surrounds the pump body to form the pump liquid cavity. The second pump cover is placed on the other end of the pump body and surrounds the pump body and the shielding sleeve to form the stator cavity and the rotor cavity.

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