Liquid pump

Abstract

This application discloses a liquid pump, including a pump body, a rotor assembly, and multiple blades. The pump body has a pump liquid chamber, a receiving chamber located on one axial side of the pump liquid chamber for accommodating the stator, and a heat dissipation chamber located radially outside the stator for dissipating heat from the stator. The rotor assembly is located at the center of the stator, and an impeller assembly is connected to the axial end of the rotor assembly. The impeller assembly is located inside the pump liquid chamber, and a through groove is formed in the wall of the pump liquid chamber, which communicates with the heat dissipation chamber through the through groove. The multiple blades are distributed circumferentially along the through groove, and the angle between the chord line of the multiple blades and the axis of the pump body gradually increases along the rotation direction of the rotor assembly. The liquid pump of this application achieves self-circulation of liquid flow under pressure difference, eliminating the need for additional piping structures, simplifying manufacturing, reducing fluid flow resistance, and the multiple blades forming a helical structure, thereby more effectively utilizing the momentum of the fluid, generating a stronger vortex effect, and further improving heat dissipation efficiency.

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 the liquid pump by circulating and cooling the liquid, ensuring that the liquid pump operates stably within the 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, comprising:

[0009] The pump body is provided with a pump liquid chamber, a receiving chamber located on one axial side of the pump liquid chamber for accommodating the stator, and a heat dissipation chamber located on the radial outer side of the stator for dissipating heat from the stator.

[0010] A rotor assembly is disposed at the center of the stator, and an impeller assembly is connected to the axial end of the rotor assembly, the impeller assembly being located within the pump fluid chamber;

[0011] The pump fluid chamber has a through groove in its wall, and the pump fluid chamber communicates with the heat dissipation chamber through the through groove;

[0012] Multiple blades are distributed circumferentially along the through groove, and the angle between the chord of the multiple blades and the axis of the pump body gradually increases along the rotation direction of the rotor assembly.

[0013] In some embodiments, the axial cross-section of each blade is an asymmetric airfoil.

[0014] In some embodiments, the thickness of each blade gradually increases and then gradually decreases along the axial direction of the pump body.

[0015] In some embodiments, each blade includes a top surface and a bottom surface disposed opposite to each other. The bottom surface is connected to the end of the through groove near the pump body axis, and the top surface is connected to the end of the through groove away from the pump body axis. The shortest line connecting the two ends of the top surface does not coincide with the shortest line connecting the two ends of the bottom surface.

[0016] In some embodiments, the angle between the shortest line connecting the two ends of the top surface and the shortest line connecting the two ends of the bottom surface ranges from 5° to 20°.

[0017] In some embodiments, the angle between the chord of each blade and the axis of the pump body is in the range of 15°≤a≤75°.

[0018] In some embodiments, the plurality of blades are evenly distributed at circumferential intervals along the through slot.

[0019] In some embodiments, the radial dimension of the through slot gradually increases along the rotation direction of the rotor assembly.

[0020] In some embodiments, the pump body includes a main body, 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 main body. The cylindrical shell is fitted onto the main 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 disposed on one end of the main body and surrounds the main body to form the pump liquid cavity. The second pump cover is disposed on the other end of the main body and surrounds the main body to form the receiving cavity.

[0021] In some embodiments, the liquid pump further includes a shielding sleeve disposed at the center of the stator, and the shielding sleeve, together with the inner wall of the main body and the inner wall of the second pump cover, forms a rotor cavity, and the rotor assembly is disposed within the rotor cavity.

[0022] Compared with the prior art, the liquid pump provided in this application has at least the following beneficial effects:

[0023] 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. This achieves liquid self-circulation, improves heat dissipation efficiency, reduces the need for an external power source, and eliminates the need for... Adding a pipeline structure helps reduce the size of the liquid pump, making manufacturing simpler and reducing costs. It also reduces fluid flow resistance, thereby reducing energy loss. Furthermore, this application has multiple blades to accelerate and pressurize the fluid through the centrifugal force generated by the multiple blades. The angle between the chord of the multiple blades and the axis of the pump body gradually increases along the rotation direction of the rotor assembly. During rotation, it can generate rotational torque and form a spiral structure, thereby making more effective use of the fluid momentum. By using the internal pressure difference principle, it generates a stronger vortex effect, enhances the heat transfer rate, and further improves heat dissipation efficiency, thus improving the overall performance of the system using this liquid pump. Attached Figure Description

[0024] Figure 1 This is a schematic diagram of the structure of a liquid pump provided in an embodiment of this application;

[0025] Figure 2 A cross-sectional view of a liquid pump provided in an embodiment of this application;

[0026] Figure 3 A schematic diagram of the structure of the liquid pump body provided in an embodiment of this application;

[0027] Figure 4 A top cross-sectional view of the impeller of a liquid pump provided in an embodiment of this application;

[0028] Figure 5 This is a structural schematic diagram of the liquid pump body provided in an embodiment of this application from another perspective.

[0029] Figure label:

[0030] 1. Stator; 2. Impeller assembly; 3. Rotor assembly; 31. Rotor; 32. Shaft; 320. Protrusion; 4. Pump liquid chamber; 41. Through groove; 42. Flow channel; 5. Blade; 51. Top surface; 52. Bottom surface; 6. Heat dissipation chamber; 7. Pump body; 71. Main body; 710. Liquid outlet; 72. Heat dissipation annular groove; 8. Shell; 9. First pump cover; 91. Liquid inlet; 10. Second pump cover; 11. Receiving cavity; 110. Annular protrusion; 12. Rotor cavity; 13. Oil nozzle; 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

[0031] 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.

[0032] 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.

[0033] 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.

[0034] 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.

[0035] Therefore, this application provides a liquid pump to improve the above-mentioned problems.

[0036] Reference Figures 1-4 As shown, Figure 1 This is a schematic diagram of the structure of the 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 structure of the liquid pump body provided in an embodiment of this application. Figure 4 This is a top cross-sectional view of the impeller of a liquid pump provided in an embodiment of this application. This embodiment discloses a liquid pump 100, including a pump body 7, a rotor assembly 3, and multiple impellers 5. The pump body 7 has a pumping chamber 4, an inlet 91 and an outlet 710 communicating with the pumping chamber 4, a receiving cavity 11 located on one axial side of the pumping chamber 4 for accommodating a stator 1, and a heat dissipation cavity 6 located radially outside the stator 1 for dissipating heat from the stator 1. The rotor assembly 3 is disposed at the center of the stator 1, and an impeller assembly 2 is connected to the axial end of the rotor assembly 3. The impeller assembly 2 is disposed in the pumping chamber 4. A through groove 41 is formed in the wall of the pumping chamber 4, allowing the formation of a high-pressure zone and a low-pressure zone. The liquid pressure in the high-pressure zone is greater than the liquid pressure in the low-pressure zone. The pumping chamber 4 communicates with the heat dissipation cavity 6 through the through groove 41, meaning the heat dissipation cavity 6 connects the high-pressure zone and the low-pressure zone of the pumping chamber 4 through the through groove 41. Multiple blades 5 are distributed circumferentially along the through groove 41, and the angle α between the chord line of the multiple blades 5 and the axis of the pump body 7 gradually increases along the rotation direction of the rotor assembly 3. Here, the axis of the pump body 7 is z, the chord line of the blades 5 is b, the chord line of the blades 5 is the line connecting the two ends on the axial section, the sum of the included angle α and the installation angle of the blades 5 is 90°, and the axial direction is... Figure 2 The X direction and the radial direction are... Figure 2 in the Y direction.

[0037] 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 the impeller assembly 2. The principle of pressure difference refers to the difference in water pressure along the flow direction. When the impeller assembly 2 rotates, the rotational motion causes water flow. The area near the center line of the impeller assembly 2 is subject to low water pressure, while the area near the outer diameter of the impeller assembly 2 is affected by the water pressure of the high-pressure turbulent zone, resulting in a pressure difference. Furthermore, the interaction between the impeller assembly 2 and the inner wall of the 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 the impeller assembly 2 rotation. This causes the liquid to flow from the high-pressure zone to the low-pressure zone, and then 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 assembly 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.

[0038] In this embodiment, the impeller assembly 2 includes two impellers coaxially arranged in the axial direction, so that the liquid pump 100 can obtain a higher head and a larger flow rate, thereby improving the working efficiency. In specific applications, the number of impellers can be set according to the flow rate required for liquid cooling, and is not limited here.

[0039] In this embodiment, the liquid pump 100 also includes a guide vane 23, which is disposed between two impellers to guide the flow of liquid. By combining the dynamic movement of the impellers 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.

[0040] 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.

[0041] In this embodiment, there are seven 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.

[0042] In this embodiment, the angle α between the chord of each blade 5 and the axis of the pump body 7 is in the range of 15°≤a≤75°, so as to reduce the situation where excessively large angles lead to a decrease in fluid output flow and thus reduce efficiency, and reduce the situation where excessively small angles lead to insufficient fluid contact with the blades 5 and thus reduce efficiency, thereby improving the working efficiency of the liquid pump 100.

[0043] In this embodiment, the pump chamber 4 has a circumferentially extending through groove 41 on its cavity wall. The pump chamber 4 is connected to the heat dissipation chamber 6 through the through groove 41, and a high-pressure zone and a low-pressure zone can be formed within the pump chamber 4. The liquid pressure in the high-pressure zone is greater than the liquid pressure 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 chamber 4 through the through groove 41, when the liquid pump is working, under the action of pressure difference, the liquid in the pump 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 chamber 4 through the through groove 41, so that the liquid circulates repeatedly from high pressure to low pressure to remove the heat from the heat dissipation chamber 6. This achieves liquid self-circulation, improves heat dissipation efficiency, and reduces reliance on external power sources. The system eliminates the need for additional piping, reducing the size of the liquid pump 100, simplifying manufacturing, lowering costs, and reducing fluid flow resistance, thereby reducing energy loss. Furthermore, the system incorporates multiple blades 5 to accelerate and pressurize the fluid through centrifugal force. The angle between the chord of the multiple blades 5 and the axis of the pump body 7 gradually increases along the rotation direction of the rotor assembly 3, generating rotational torque and forming a spiral structure. This allows for more effective utilization of fluid momentum, utilizing the internal pressure difference principle to generate a stronger vortex effect, enhancing heat transfer rate, and further improving heat dissipation efficiency. Ultimately, this improves the overall performance of the system using the liquid pump 100.

[0044] Reference Figure 4 As shown, the axial cross-section of each blade 5 is an asymmetric airfoil. Compared with a symmetric airfoil, it has a smaller inflow angle when the outflow angle of each blade 5 is the same, which reduces the energy loss when water flows in, thereby effectively ensuring the efficiency of the liquid pump 100.

[0045] In this embodiment, along the axial direction of the pump body 7, the thickness of each blade 5 gradually increases and then gradually decreases, so that the blade 5 is streamlined, reducing eddies and turbulence, improving the efficiency of the liquid pump 100, and appropriately reducing the thickness of the outlet of the blade 5 can reduce wake loss, thereby further improving the efficiency of the liquid pump 100.

[0046] It should be noted that the blade 5 in this embodiment is an airfoil blade. The airfoil of this airfoil blade can be selected from the NACA airfoil series database as needed, such as NACA4406 airfoil, NACA44XX airfoil, etc., and is not limited here.

[0047] Reference Figure 3 and Figure 4 As shown, each blade 5 includes a top surface 51 and a bottom surface 52 arranged opposite to each other. The bottom surface 52 is connected to the end of the through groove 41 near the axis of the pump body 7, and the top surface 51 is connected to the end of the through groove 41 away from the axis of the pump body 7. The shortest line connecting the two ends of the top surface 51 (i.e., the chord of the top surface 51) does not coincide with the shortest line connecting the two ends of the bottom surface 52 (i.e., the chord of the bottom surface 52). That is, the blade 5 is twisted in the radial direction to increase the load-bearing capacity of the blade 5 and improve the reliability of the liquid pump 100. Moreover, at different positions of the blade 5, the twisted state optimizes the angle between the blade 5 and the flow direction, thereby minimizing fluid dynamic losses and improving the working efficiency of the liquid pump 100.

[0048] In this embodiment, the angle formed by the shortest line connecting the two ends of the top surface 51 and the shortest line connecting the two ends of the bottom surface 52 is in the range of 5° to 20°, so as to reduce the situation where eddies are easily generated when the angle is too large or too small, thereby affecting the overall performance and efficiency of the liquid pump 100.

[0049] Reference Figure 3 and Figure 5 As shown, Figure 5 This is a schematic diagram of the liquid pump body from another perspective, provided in an embodiment of this application. 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), promoting the formation of vortices, increasing the liquid flow rate, and enabling 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.

[0050] In this embodiment, the inner wall of the pump liquid chamber 4 is formed with a flow channel 42 extending along the Archimedean spiral. In the radial direction, the flow channel 42 is located between the inner wall of the pump liquid chamber 4 and the through groove 41. The axial direction of the flow channel 42 is consistent with the axial direction of the impeller assembly 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 assembly 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.

[0051] 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 assembly 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.

[0052] Reference Figure 1 and Figure 2 As shown, the pump body 7 includes a main body 71, a cylindrical shell 8, a first pump cover 9, a second pump cover 10, and a shielding sleeve 20. The main body 71 has an outlet 710 communicating with the pump liquid chamber 4, and a heat dissipation annular groove 72 is formed on the radially outer side of the main body 71. The cylindrical shell 8 is fitted onto the main body 71 and seals the heat dissipation annular groove 72, the groove of which is a heat dissipation chamber 6. The first pump cover 9 is connected to the main body 71 by a stud 21 and covers one end of the main body 71, forming the pump liquid chamber 4 with the main body 71, 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 main body 71 by a stud 21 and covers the other end of the main body 71, forming a receiving cavity 11 with the main body 71. The cavity wall of the receiving cavity 11 is provided with an annular protrusion 110. The shielding sleeve 20 is sleeved on the annular protrusion 110 and located at the center of the stator 1, so that the shielding sleeve 20, the inner wall of the receiving cavity 11 and the inner wall of the second pump cover 10 surround to form a rotor cavity 12. The rotor assembly 3 is disposed in the rotor cavity 12. The shielding sleeve 20 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.

[0053] In this embodiment, the inlet 91 is located at the radial center of the impeller assembly 2, and the outlet 710 is located at the radial outer end of the impeller assembly 2, so as to output fluid 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 710; or a pumping form with a radial inlet 91 and a radial outlet 710; or a pumping form with a radial inlet 91 and an axial outlet 710.

[0054] 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.

[0055] In this embodiment, the main body 71 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 receiving 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 heat is carried away by the liquid in the heat dissipation cavity 6, 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 main body 71. This allows the control components to be placed on the outside of the main body 71 for convenient heat dissipation and maintenance.

[0056] Continue to refer to Figure 1 and Figure 2 As shown, the rotor assembly 3 includes a rotor 31 and a shaft 32, with the rotor 31 disposed within the rotor cavity 12. The shaft 32 is rotatably connected to the body 71 via a bearing 22, which reduces friction between the shaft 32 and the body 71 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 sleeved on 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.

[0057] 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 body 71 to ensure the sealing between the rotating shaft 32 and the body 71 when the rotating shaft 32 passes through the body 71, thereby ensuring the sealing between the pump liquid chamber 4 and the rotor chamber 12.

[0058] Reference Figure 2As 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 within the groove and abuts against the inner wall of the body 71 to ensure a tight seal between the first pump cover 9 and the body 71. The outer wall surface of the annular protrusion 110 has a groove, and the sealing ring 19 is disposed within the groove and abuts against the inner wall of the shielding sleeve 20 to ensure a tight seal 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 within the groove and abuts against the inner wall of the body 71 to ensure a tight seal between the second pump cover 10 and the body 71. 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, where the sealing ring 19 is disposed within the groove and abuts against the inner wall of the shielding sleeve 20 to ensure a tight seal in the rotor cavity 12.

[0059] Reference Figure 3 As shown, the cavity wall of the heat dissipation annular groove 72 is provided with multiple first fins 15 at intervals. The cavity wall of the heat dissipation annular groove 72 is the wall surface of the heat dissipation annular groove 72 along the radial direction near the stator 1. The inner wall surface of the stator 1 cavity is provided with multiple second fins 16 at intervals. The heat exchange area is increased by the first fins 15 and the second fins 16, thereby utilizing the synergistic effect of the finned heat dissipation structure and liquid cooling to improve heat dissipation efficiency. The fins can also play a role in turbulence, improving heat exchange capacity and thus improving heat dissipation efficiency. The multiple first fins 15 and the multiple second fins 16 can be arranged at equal intervals or at unequal intervals.

[0060] 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.

[0061] In this embodiment, each first fin 15 is inclined, that is, the angle between the first fin 15 and the cavity wall of the pumping 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 cavity wall of the pumping chamber 4 can also be equal to 90°.

[0062] 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 main body 71, and the guide shroud and the second pump cover 10 enclose a space for the fan impeller to work. 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.

[0063] 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 opposite to the main body 71, so as to further increase the heat exchange area and thus further improve the heat exchange efficiency.

[0064] 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 assembly 2 to rotate. The centrifugal force of the rotation of the impeller assembly 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 liquid self-circulation. The heat extracted from the heat dissipation chamber 6 can be extracted from the outlet 710 of the pump liquid chamber 4, thereby achieving continuous heat dissipation and meeting the requirements of high heat dissipation rate.

[0065] 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 in that, include: The pump body is provided with a pump liquid chamber, a receiving chamber located on one axial side of the pump liquid chamber for accommodating the stator, and a heat dissipation chamber located on the radial outer side of the stator for dissipating heat from the stator. A rotor assembly is disposed at the center of the stator, and an impeller assembly is connected to the axial end of the rotor assembly, the impeller assembly being located within the pump fluid chamber; The pump fluid chamber has a through groove in its wall, and the pump fluid chamber is connected to the heat dissipation chamber through the through groove. Multiple blades are distributed circumferentially along the through groove, and the angle between the chord of the multiple blades and the axis of the pump body gradually increases along the rotation direction of the rotor assembly.

2. The liquid pump of claim 1, wherein, The axial cross-section of each blade is an asymmetric airfoil.

3. The liquid pump of claim 1, wherein, Along the axial direction of the pump body, the thickness of each blade gradually increases and then gradually decreases.

4. The liquid pump of claim 1, wherein, Each blade includes a top surface and a bottom surface arranged opposite to each other. The bottom surface is connected to the end of the through groove near the pump body axis, and the top surface is connected to the end of the through groove away from the pump body axis. The shortest line connecting the two ends of the top surface does not coincide with the shortest line connecting the two ends of the bottom surface.

5. The liquid pump of claim 4, wherein, The angle between the shortest line connecting the two ends of the top surface and the shortest line connecting the two ends of the bottom surface ranges from 5° to 20°.

6. The liquid pump of claim 1, wherein, The angle between the chord of each blade and the axis of the pump body is in the range of 15°≤a≤75°.

7. The liquid pump of claim 1, wherein, The multiple blades are evenly distributed at circumferential intervals along the through groove.

8. The liquid pump of claim 1, wherein, 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 pump body includes a main body, 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 main body. The cylindrical shell is fitted onto the main 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 main body and surrounds the main body to form the pump liquid cavity. The second pump cover is placed on the other end of the main body and surrounds the main body to form the receiving cavity.

10. The liquid pump of claim 9, wherein, The liquid pump also includes a shielding sleeve, which is disposed at the center of the stator, and the shielding sleeve, together with the inner wall of the main body and the inner wall of the second pump cover, forms a rotor cavity, and the rotor assembly is disposed in the rotor cavity.

Images